CN208605570U - A kind of novel combination type non-circular gear infinitely variable speed transmission - Google Patents
A kind of novel combination type non-circular gear infinitely variable speed transmission Download PDFInfo
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- CN208605570U CN208605570U CN201820697234.XU CN201820697234U CN208605570U CN 208605570 U CN208605570 U CN 208605570U CN 201820697234 U CN201820697234 U CN 201820697234U CN 208605570 U CN208605570 U CN 208605570U
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Abstract
The utility model discloses a kind of novel combination type non-circular gear infinitely variable speed transmissions, it include: a commutation planet row (100), the phase regulator (200), a synchronized reversed planet row being mutually connected together, a non-circular gear shares input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms.A kind of novel combination type non-circular gear infinitely variable speed transmission disclosed by the utility model, it can reliably eliminate power cycle problem present in non-circular gear shifting mechanism, increase transmission efficiency, guarantee that there is good transmission performance, be conducive to widely promote and apply, be of great practical significance.
Description
Technical field
The utility model relates to technical field of mechanical transmission, more particularly to a kind of stepless change of novel combination type non-circular gear
Fast transmission device.
Background technique
Currently, variable transmission refers under the control of outside, transmission ratio is able to achieve between input shaft and output shaft one
A kind of kind of drive for determining consecutive variations in range is the development trend of the following speed changer.With the continuous deepening of research, non-circular
Gear stepless variable drive structure causes the extensive of people due to having the advantages that high-power, big torque, high efficiency, wide transmission ratio
Pay attention to.
The main thought for realizing variable speed using non-circular gear and box of tricks is, by specific transmission ratio requirement, specially
Two non-circular gears pair with specific transmission ratio function are designed, and output it the two-way input as box of tricks, through difference
After fast mechanism superposition, realize that transmission ratio is constant within the scope of certain angle, by phase adjusting device, to change two non-knuckle-tooth
The relative position of wheel pair, and then realize resultant gear ratio consecutive variations, then the gear as multiple groups is combined, according to
The secondary continuous transmission coordinated within the scope of 360 ° of relay realization.
The gear that reference surface is not surface of revolution it should be noted that non-circular gear is also special shape gear, it and it is another
After one gear composition gear pair (gear mesh), in engagement process, instantaneous angular velocity by certain set movement than being advised
It restrains and changes.
But existing non-circular gear infinitely variable speed transmission, generally there is inevitable circulating power, so that passing
Efficiency of movement is lower, has seriously affected actual transmission performance.
Therefore, there is an urgent need to develop a kind of technologies out, can reliably eliminate present in non-circular gear shifting mechanism
Power cycle problem increases transmission efficiency, guarantees there is good transmission performance.
Utility model content
In view of this, the purpose of the utility model is to provide a kind of novel combination type non-circular gear variable transmission dresses
It sets, can reliably eliminate power cycle problem present in non-circular gear shifting mechanism, increase transmission efficiency, guarantee have
Good transmission performance is conducive to widely promote and apply, be of great practical significance.
For this purpose, the utility model provides a kind of novel combination type non-circular gear infinitely variable speed transmission, comprising: mutually
A commutation planet row, a phase regulator, the synchronized reversed planet row, a non-circular gear being connected together
Share input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms.
Wherein, the commutation planet row includes planet row sun gear, planet row shell, planet row gear ring, planet row engagement
Set, left-end components, planet row planet carrier and planet row ring gear；
Planet row sun gear passes through the inside gear teeth meshing of the gear teeth and planet row ring gear on the outside of it, planet row ring gear and row
Star ranks carrier and is connected, the gear teeth meshing of the gear teeth and planet row gear ring on the outside of planet row ring gear；
The planet row left end of sun wheel is connected with and its integrally formed primary input axis.
It is equipped with endless v slot on the right side of the left-end components outer end, is key connection between inner end and primary input axis outer end；
Outer end portion is equipped with endless v slot on the right side of planet row clutch collar, for the endless v slot knot on the left of the shell
It closes.
Wherein, it includes: the first non-circular driving gear, the second non-circular master that the non-circular gear, which shares input and output transmission mechanism,
The non-circular driving gear of moving gear, third and cylinder driven gear；
First input shaft an of horizontal distribution is fixedly installed on the left of the first non-circular driving gear；
The second input shaft is fixedly installed on the left of the second non-circular driving gear；
Third input shaft is fixedly installed on the left of the non-circular driving gear of third；
The third input shaft is inserted into second input shaft, and second input shaft is inserted into first input
In axis；
Main output shaft is fixedly installed on the right side of the cylinder driven gear.
Wherein, non-circular gear branch transmission mechanism described in every group includes: the first non-circular driven gear, the second non-circular driven tooth
Wheel, the non-circular driven gear of third and cylinder driving gear, in which:
The first non-circular driven gear is intermeshed with the described first non-circular driving gear, and the two forms the first non-knuckle-tooth
Wheel pair；
The second non-circular driven gear is intermeshed with the described second non-circular driving gear, and the two forms the second non-knuckle-tooth
Wheel pair；
The non-circular driven gear of third and the non-circular driving gear of the third are intermeshed, and the two forms the first non-knuckle-tooth
Wheel pair；
The cylinder driving gear and the cylinder driven gear are intermeshed；
It extends transversely through in the second non-circular driven gear and the non-circular driven gear of third through the second jackshaft；
The first intermediate connecting shaft is fixedly installed on the left of the cylinder driving gear；
The first non-circular driven gear, the second non-circular driven gear, the non-circular driven gear of third and cylinder driving gear
In extend transversely through and be provided with an intermediate supports axis, and the intermediate supports axis is turned left to sequentially pass through among by first from the right side and be connected
Spindle and the second jackshaft.
Wherein, it is provided with first clutch between the described second non-circular driven gear and the non-circular driven gear of third, it is described
A box of tricks is provided between the non-circular driven gear of third and the cylinder driving gear.
Wherein, an one-way clutch is additionally provided between second jackshaft and the planet carrier of box of tricks.
Wherein, the box of tricks includes box of tricks gear ring, box of tricks planet carrier and box of tricks sun gear.
Wherein, first input shaft and the first non-circular driving gear are structure as a whole, the first non-circular driven gear
It is connected by spline with intermediate supports axis, the intermediate supports axis passes through the box of tricks sun gear in spline and box of tricks
It is connected；
Second jackshaft is connected by one-way clutch with box of tricks planet carrier；
130 ° of phase phase difference of second non-circular driving gear and the non-circular driving gear of third；
It is structure as a whole between the cylinder driven gear and main output shaft.
Wherein, the phase regulator is constituted by double leaf oscillating motor by stator and rotor；
The synchronized reversed planet arrangement mechanism is using double internal-gearing planet gear mechanisms, too including synchronized reversed planet row
The planet carrier of sun wheel, the gear ring of synchronized reversed planet row and synchronized reversed planet row；
It is key connection between the gear ring and the stator of the synchronized reversed planet row；
The stator and the first input shaft are key connection；
It is key connection between the planet carrier and the rotor of double internal-gearing planet gear mechanisms；
It is key connection between the rotor and the second input shaft；
It is key connection between the sun gear and third input shaft of the synchronized reversed planet row.
It wherein, further include at least one auxiliary transmission, the auxiliary transmission is connected with the main output shaft；
Second input shaft and the second non-circular driving gear are an integral molding structure, and the third input shaft and third are non-
Circle driving gear is an integral molding structure.
By the above technical solution provided by the utility model as it can be seen that compared with prior art, the utility model provides
A kind of novel combination type non-circular gear infinitely variable speed transmission, can reliably eliminate in non-circular gear shifting mechanism and exist
Power cycle problem, increase transmission efficiency, guarantee have good transmission performance, be conducive to widely promote and apply, have
Great production practices meaning.
Detailed description of the invention
Fig. 1 is a kind of stereochemical structure of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Schematic diagram；
Fig. 2 is any one group in a kind of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Non-circular gear branch transmission mechanism and non-circular gear share input driver structure, non-circular gear shares output transmission mechanism and change
Exploded perspective structural schematic diagram between planet row, synchronized reversed planet row, phase regulator；
Fig. 3 is any one group in a kind of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Non-circular gear branch transmission mechanism and non-circular gear share input driver structure, non-circular gear shares output transmission mechanism and change
To cross-sectional view when cooperating between planet row, synchronized reversed planet row, phase regulator；
Fig. 4 is the planet that commutates in a kind of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
The cross-sectional view of row；
Fig. 5 is synchronized reversed in a kind of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
The cross-sectional view of planet row and phase regulator；
Fig. 6 is phase adjusted in a kind of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Device and and synchronized reversed planet row exploded perspective structural schematic diagram；
Fig. 7 is any one group in a kind of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Non-circular gear branch transmission mechanism and non-circular gear share input driver structure, non-circular gear shares phase between output transmission mechanism
Mutually cross-sectional view when cooperation；
Fig. 8 is a kind of power transmitting of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Route simplified schematic diagram；
Fig. 9 is that a kind of transmission ratio of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model becomes
Change range schematic diagram；
Figure 10 is a kind of total output of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Gear range schematic diagram；
Figure 11 is a kind of specific reality of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Example is applied when taking general parameters phase difference is 0 °, two non-circular gears to and non-circular gear stepless speed changing mechanism output transmission ratio it is reciprocal
Image；
Figure 12 is a kind of specific reality of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Apply example take special parameter phase difference be 0 ° when, two non-circular gears to and non-circular gear stepless speed changing mechanism output transmission ratio fall
Number image；
Figure 13 is a kind of specific reality of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Apply example take special parameter phase difference be -130 ° when, two non-circular gears to and non-circular gear stepless speed changing mechanism output transmission
Compare inverse image；
Figure 14 is a kind of specific reality of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Apply example take special parameter phase difference be 130 ° when, two non-circular gears to and non-circular gear stepless speed changing mechanism export transmission ratio
Inverse image；
Figure 15 is a kind of specific reality of novel combination type non-circular gear infinitely variable speed transmission provided by the utility model
Example is applied when taking special parameter, it is total to export transmission ratio image；
In figure, 100 be commutation planet row；200 be phase regulator；
2 be cylinder driven gear；3 be the first non-circular driving gear；
31 be the first input shaft, and 1201 be the second input shaft, and 1202 be third input shaft；
4 be the first non-circular driven gear；5 be intermediate supports axis；6 be cylinder driving gear, and 61 be the first intermediate connecting shaft；
7 be box of tricks gear ring；8 be box of tricks planet carrier；9 be box of tricks sun gear；
10 be one-way clutch；110 be the second jackshaft, and 111 be the second non-circular driven gear；
112 be the non-circular driven gear of third；121 be the second non-circular driving gear；
122 be the non-circular driving gear of third；130 be first clutch；
11 be planet row sun gear；12 be planet row shell；13 be planet row gear ring；14 be planet row planet carrier, and 16 are
Planet row clutch collar, 17 be planet row ring gear；1101 be main input shaft；1601 be left-end components；
141 be the sun gear of synchronized reversed planet row；142 be the gear ring of synchronized reversed planet row；143 be rotor；144
For stator；145 be the planet carrier of synchronized reversed planet row.
Specific embodiment
In order to make those skilled in the art better understand the scheme of the utility model, with reference to the accompanying drawing and embodiment
The utility model is described in further detail.
Referring to Fig. 1 to Fig. 8, the utility model provides a kind of novel combination type non-circular gear infinitely variable speed transmission,
Comprising: a synchronized reversed row of the phase regulator 200, one of commutation planet row 100, one being mutually connected together
Star row, a non-circular gear share input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms.
In the present invention, in specific implementation, the commutation planet row 100 is double internal-gearing planet gear mechanisms, is used
In control forward gear, reverse gear, neutral gear operating condition, specifically include planet row sun gear 11, planet row shell 12, planet row gear ring 13,
Planet row planet carrier 14, left-end components 1601, primary input axis 1101, planet row planet carrier 14) and planet row ring gear 17.Wherein,
Planet row sun gear 11 be input element, planet row planet carrier 14 be output element, and planet row gear ring 13 be equipped with can be axial
Mobile planet row clutch collar 16.
For the utility model, the commutation planet row 100 includes planet row sun gear 11, planet row shell 12, planet
Toothrow circle 13, planet row planet carrier 14, planet row clutch collar 16, planet row ring gear 17 and primary input axis 1101 and left part
Part 1601.
It should be noted that having double internal-gearing planet gear mechanisms, double internal messing rows in the commutation planet row 100
Star gear mechanism is made of planet row sun gear 11, planet row planet carrier 14, planet row ring gear 17 and planet row gear ring 13, is
Its internal structure, common structure is no longer discussed in detail in existing mechanism herein are as follows: planet row sun gear 11 passes through on the outside of it
The inside gear teeth meshing of the gear teeth and planet row ring gear 17, planet row ring gear 17 and planet row planet carrier 14 are connected, planet row ring gear
The gear teeth meshing of the 17 outside gear teeth and planet row gear ring 13.
In double internal-gearing planet gear mechanisms, 11 left end of planet row sun gear is connected with defeated with its integrally formed master
Enter axis 1101.
It is equipped with endless v slot on the right side of 1601 outer end of left-end components, is key connection between 1101 outer end of inner end and primary input axis,
Same rotational speed；
16 right side outer end portion of planet row clutch collar is equipped with endless v slot, for the cyclic annular V with 12 left side of shell
Type groove combines.
It should be noted that 16 right side outer end portion of planet row clutch collar is equipped with endless v slot, planet row clutch collar 16 is left
Side inner end portion is equipped with endless v slot, and inner end is equipped with the keyway in axial splines and gear ring 13 and is connected, can be with respect to planet
Toothrow circle 13 moves axially, but the two is circumferentially fixed, cannots rotate relative to each other.Planet row clutch collar 16 moves axially through outside
Executing agency realizes, no matter moves to left to move to right and is all connected by the axial splines of inner end and planet row gear ring 13, keeps turning with revolving speed
It is dynamic.
In addition, connecting between gear ring 142 in planet carrier 14 and synchronized reversed planet row in commutation planet row 100 for key
It connects.Other component except other parts discord commutation planet row 100 has connection relationship.
For the planet row 100 that commutates, operation process are as follows: the machine thus of planet row sun gear 11 in commutation planet row 100
The power input of structure, power are input to planet row sun gear 11, the rotation of planet row sun gear.Again because of planet row sun gear 11
By the gear teeth meshing of 17 inside of the gear teeth and planet row ring gear, planet row ring gear 17 and planet carrier 14 are connected, planet row ring gear 17
The gear teeth meshing of the outside gear teeth and planet row gear ring 13, so planet row sun gear drives planet row by planet row ring gear 17
Gear ring 13 and planet row gear ring planet carrier 14 rotate.
When planet row clutch collar 16 moves to right under the action of exterior operator, pass through the cyclic annular V of right side outer end face
The endless v slot in 12 left side of type groove and shell combines, and the two keeps same rotational speed, and planet row gear ring 13 passes through planet row at this time
Clutch collar 16 and planet row shell 12 keep same rotational speed.Because shell can not rotate, gear ring is static at this time, at this moment root
Kinetic characteristic equation according to double internal-gearing planet gear mechanisms is as follows:
nS+(k-1)nH-knR=0；
Wherein nsFor sun wheel speed, nHFor planet carrier revolving speed, nRFor the revolving speed of gear ring.
K=2 is taken, when planet row sun gear 11 and planet row planet carrier 14 rotate in same direction at the same speed, transmission ratio 1.
When planet row clutch collar 16 moves to left under the action of exterior operator, planet row combined cover 16 passes through left side
Endless v slot on 1601 right side of endless v slot and left-end components of inner face combines, and the two keeps same rotational speed, left end
The inner end and 1101 outer end of primary input axis of component 1601 are key connection, and primary input axis 1101 and planet row sun gear 11 are integrated knot
Structure, at this moment planet row gear ring 13 passes through planet row clutch collar 16, left-end components 1601 and primary input axis 1101 and the planet row sun
Wheel 11 keeps same rotational speed.
At this moment according to the kinetic characteristic equation of double internal-gearing planet gear mechanisms:
nS+(k-1)nH-knR=0；
Sun gear 11 and planet carrier 14 is taken to rotate in same direction at the same speed, transmission ratio 1.
Therefore, transmission ratio may be implemented by moving left and right for planet row clutch collar 16 for the planet row 100 that commutates
It is positive and negative 1 transmission.
In the present invention, in specific implementation, it includes: first non-that the non-circular gear, which shares input and output transmission mechanism,
Circle driving gear 3, the second non-circular driving gear 121, the non-circular driving gear 122 of third and cylinder driven gear 2；
The left side of the first non-circular driving gear 3 is fixedly installed first input shaft 31 an of horizontal distribution；
The left side of the second non-circular driving gear 121 is fixedly installed the second input shaft 1201；
The left side of the non-circular driving gear 122 of third is fixedly installed third input shaft 1202；
The third input shaft 1202 is inserted into second input shaft 1201, and second input shaft 1201 is inserted into
Into first input shaft 31；
The right side of the cylinder driven gear 2 is fixedly installed main output shaft 21.
In the present invention, in specific implementation, non-circular gear branch transmission mechanism described in every group include: first it is non-circular from
Moving gear 4, the second non-circular driven gear 111, the non-circular driven gear 112 of third and cylinder driving gear 6, in which:
The first non-circular driven gear 4 is intermeshed with the described first non-circular driving gear 3, and the two composition first is non-circular
Gear mesh；
The second non-circular driven gear 111 is intermeshed with the described second non-circular driving gear 121, the two composition second
Non-circular gear pair；
The non-circular driven gear 112 of third is intermeshed with the non-circular driving gear 122 of the third, the two composition first
Non-circular gear pair；
The cylinder driving gear 6 is intermeshed with the cylinder driven gear 2；
It extends transversely through in the second non-circular driven gear 111 and the non-circular driven gear 112 of third through the second jackshaft
110；
The left side of the cylinder driving gear 6 is fixedly installed the first intermediate connecting shaft 61；
The first non-circular driven gear 4, the second non-circular driven gear 111, the non-circular driven gear 112 of third and cylinder
Extended transversely through in driving gear 6 and be provided with an intermediate supports axis 5, and the intermediate supports axis 5 turn left from the right side sequentially pass through it is logical
Cross the first intermediate connecting shaft 61 and the second jackshaft 110.
It should be noted that in the present invention, 61 outside left end of the first intermediate connecting shaft and box of tricks gear ring 7 it
Between for key connection, outside right end and cylinder driving gear 6 are structure as a whole, outside 61 inner end of the first intermediate connecting shaft and support shaft 5
It is equipped with needle bearing between side, can relatively rotate.
It should be noted that its exterior is equipped with shells for the utility model, it is defeated to share input to fixed non-circular gear
The positional relationship of transmission mechanism and three groups of non-circular gear branch transmission mechanisms out.
In specific implementation, first is provided between the second non-circular driven gear 111 and the non-circular driven gear 112 of third
Clutch 130 is provided with a box of tricks between the non-circular driven gear 112 of third and the cylinder driving gear 6.
In specific implementation, an one-way clutch is additionally provided between second jackshaft 110 and box of tricks planet carrier 8
Device 10.
In specific implementation, the box of tricks include box of tricks gear ring 7, box of tricks planet carrier 8 and box of tricks too
Sun wheel 9.
It should be noted that first clutch 130 and one-way clutch 10 are conventionally known structures.First clutch
130 to control between the non-circular driven gear 111 and 112 of the second non-circular driven gear, third only one can with second in
Between axis 110 engagement, another separation.And one-way clutch 10, for controlling the second jackshaft 110 and box of tricks planet carrier
8 connection status when work, realizes the connection of the second jackshaft 110 and box of tricks planet carrier 8, when not working, in second
Between axis 110 and box of tricks planet carrier 8 be in discrete state.
In addition, according to the drive characteristic of one-way clutch 10, in non-circular gear branch transmission mechanism described in three groups, always only
There is the one-way clutch 10 in one group of non-circular gear branch transmission mechanism to work.Therefore it may be implemented to allow three groups of non-circular gears
Branch transmission mechanism carries out 360 ° of relay work.
It should be noted that the box of tricks is existing knot using double inner engaging gear mechanisms for the utility model
Structure.Wherein, 9 inner end of box of tricks sun gear of the box of tricks is connected by spline and intermediate supports axis 5, box of tricks
Box of tricks planet carrier 8 and one-way clutch 10 are key connection, connection among the box of tricks gear ring 7 of box of tricks 7 and first
It is key connection between 61 outside left end of axis.
In the present invention, the working principle of the box of tricks are as follows: power is through box of tricks sun gear 9 and differential
The input of 8 two-way of mechanism planet carrier, then according to its characteristic equation, the box of tricks gear ring 7 as output element is turned by certain
Speed output.Therefore, it can be inputted by the two-way of box of tricks, constant output revolving speed can be obtained according to its characteristic equation.
In specific implementation, first input shaft 31 and the first non-circular driving gear 3 are structure as a whole, and first is non-circular driven
Gear 4 is connected by spline with intermediate supports axis 5, and the intermediate supports axis 5 passes through the differential mechanism in spline and box of tricks
Structure sun gear 9 is connected.
In specific implementation, the second input shaft 1201 and the second non-circular driving gear 121 are an integral molding structure, the third
Input shaft 1202 and the non-circular driving gear 122 of third are an integral molding structure.
In specific implementation, 130 ° of phase phase difference of the second non-circular driving gear 121 and the non-circular driving gear 122 of third.
In specific implementation, due to be connected between the second non-circular driven gear 111 and the non-circular driven gear 112 of third first from
Clutch 130, it is total in the second non-circular driven gear 111 and the non-circular driven gear 112 of third under the control of first clutch 130
There are a meeting and the engagement of the second jackshaft 110, and another is separated.
In specific implementation, second jackshaft 110 is connected by one-way clutch 10 and box of tricks planet carrier 8.
In specific implementation, box of tricks gear ring 7 is used as output element, is connected by spline and the first intermediate connecting shaft 61.
In specific implementation, it is structure as a whole between the cylinder driven gear 2 and main output shaft 21.
It should be noted that in the present invention, the box of tricks is double inner engaging gear mechanisms, and box of tricks is too
Sun wheel 9 and box of tricks planet carrier 8 are input element, and box of tricks gear ring 7 is output element, according to its kinetic characteristic equation nS
+(k-1)nH-knR=0, it is known that, the non-circular gear shifting mechanism based on adder principle that the utility model uses, there is no follow
Ring torque, transmission efficiency is high, but available gear ratios are limited in scope, and therefore, the utility model can also include that at least one is secondary
Speed changer 300, the auxiliary transmission 300 are connected with the main output shaft 21, so as to expand ratio coverage, realize
It is segmented variable speed.
In specific implementation, the binary logic speed changer that the auxiliary transmission 300 can be in series using multiple planet rows,
The non-1 transmission ratio Q of i-th planet row and using the non-circular gear shifting mechanism slowest ratio of adder principle and minimum speed ratio it
Than the relationship between q are as follows:N (natural number for being greater than zero) a planet row has 2nA gear number, it is each keep off transmission ratio it
Between strictly by geometric progression distribution be jth gear transmission ratio be Qj=qj-1(note: it is direct gear that a gear transmission ratio, which is 1).
In the present invention, in specific implementation, the phase regulator 200 is made of stator 144 and rotor 143, is used
To adjust the first non-circular gear pair that the first non-circular driving gear 3 and the first non-circular driven gear 4 form, with the second non-circular active
The relative position between the second non-circular gear pair that gear 121 and the second non-circular driven gear 111 form, and adjusting first are non-
The first non-circular gear pair that circle driving gear 3 and the first non-circular driven gear 4 form, with the non-circular driving gear 122 of third and the
The relative position between third non-circular gear pair that three non-circular driven gears 112 form.
In the present invention, the synchronized reversed planet row is anti-using double internal-gearing planet gear mechanisms, including at the same speed
To the sun gear 141, the gear ring 142 of synchronized reversed planet row and the planet carrier 145 of synchronized reversed planet row of planet row.
It should be noted that rotor 143 is connected with primary input axis 1201 (to be also equivalent in phase regulator 200
It is connected with the second non-circular driving gear 121), rotor 143 passes through with the planet carrier 145 of synchronized reversed planet row to be connect；Stator 144
It is connected with the first input shaft 31 and (is also equivalent to be connected with the first non-circular driving gear 3)；Stator 144 and synchronized reversed planet row
Gear ring 142 is connected by spline.
It should be noted that in the present invention, stator 144 and rotor 143 are actually oscillating motor.When hydraulic
When oily drive rotor 143 turns an angle, the primary input axis 1201 (gear 121) being attached thereto is driven to rotate equal angular,
And stator 144 does not move, i.e., the first non-circular driving gear 3 does not move, therefore the first non-circular driving gear 3 and the second non-circular driving gear
Phase difference is generated between 121.
In the present invention, synchronized reversed planet row and commutation planet row are mechanism of the same race, structure and connection type
It is identical with commutation planet row.
Wherein, synchronized reversed planet row, to realize the second non-circular driving gear 121 and the non-circular driving gear 122 of third
Same speed reverse movement.
In specific implementation, the planet row planet carrier 14 (output element) and synchronized reversed planet of the commutation planet row 100
The gear ring 142 of row is key connection, same to rotational speed；
It is key connection between the gear ring 142 and the stator 144 of the synchronized reversed planet row in specific implementation, it is same to turn
Speed rotation；
In specific implementation, the stator 144 and the first input shaft 31 are key connection, same to rotational speed；
In specific implementation, the planet row planet carrier 14, the gear ring 142 of synchronized reversed planet row, stator 144 respectively and
It is followed successively by key connection between first input shaft 31 of non-circular gear stepless speed changing mechanism, keeps same rotational speed.
It is key connection, same revolving speed between the planet carrier 145 and the rotor 143 of synchronized reversed planet row in specific implementation
Rotation, also, be key connection between the rotor 143 and the second input shaft 1201 of non-circular gear stepless speed changing mechanism, it is same to turn
Speed rotation；Second input shaft of the i.e. synchronized reversely planet carrier 145 of planet row, rotor 143 and non-circular gear stepless speed changing mechanism
121 are followed successively by key connection, keep same rotational speed.
In specific implementation, the third input of the sun gear 141 and non-circular gear stepless speed changing mechanism of synchronized reversed planet row
It is key connection between axis 1202, keeps same rotational speed.
According to the kinetic characteristic equation n of synchronized reversed planet rowS+(k-1)nH-knR=0, this programme takes k=2, synchronized anti-
To the planet carrier 145 of planet row and 141 same speed reverse movement of sun gear of synchronized reversed planet row, the second input shaft can be realized
1201 and third input shaft 1202 same speed reverse movement, and then realize two non-circular driving gear (the i.e. second non-circular driving gears
121 and the non-circular driving gear 122 of third) at the same speed rotate backward.
It should be noted that synchronized reversed planet row is fitted as double internal-gearing planet gear mechanisms for the utility model
Kinetic characteristic equation with double internal-gearing planet gear mechanisms is nS+(k-1)nH-knR=0, wherein nS、nH、nRRespectively too
The relative rotation speed of sun wheel, planet carrier and gear ring, this programme takes k=2, as the relative rotation speed n of gear ringRWhen being 0, have: nS=-nH, i.e.,
Realize the planet carrier 145 of synchronized reversed planet row and 141 same speed reverse movement of sun gear of synchronized reversed planet row.
In specific implementation, rotor 143 can relative stator 144 rotate, drive the second non-circular driving gear 121 and third it is non-
Circle driving gear 122 rotates backward at the same speed, to change the second non-circular gear to, third non-circular gear pair and the first non-circular gear
Pair relative position, realize variable ratio transmission.
It should be noted that for the utility model comprising 100, phase regulators of a commutation planet row
200, a synchronized reversed planet row, a non-circular gear share input and output transmission mechanism, three groups of non-circular gear branch transmissions
Mechanism and at least one auxiliary transmission share input and output transmission mechanism by non-circular gear, three groups of non-circular gear branches pass
The coordination relay of motivation structure gear can be realized the continuous transformation of 360 ° of power flows, and be set using based on adder principle
Meter input and output transmission mechanism is shared by non-circular gear, three groups of non-circular gear branch transmission mechanism gears form it is non-circular
The mode of gear stepless variable drive structure and auxiliary transmission combination, to realize segmentation variable transmission.
Wherein, non-circular gear shares input and output transmission mechanism, three groups of non-circular gear branch transmission mechanism gears etc.
The combination of non-circular gear shifting mechanism is controlled with separating by one-way clutch 10, for the company of transmission ratio within the scope of certain angle
Continue stepless variation, is then to be realized by phase regulator to change the phase relation of working two groups of non-circular gears pair.
For the utility model, it should be noted that theoretically, as long as every group of non-circular gear shifting mechanism works 120 °,
But for the continuity for keeping power, there should be certain angular superposition, the angle of practical every group of work should be greater than 120 °, in this reality
In novel, the operating angle of every group of non-circular gear shifting mechanism is set as 130 °.Therefore, amount to 390 ° to realize a whole circle
The stable drive ratio of 360 ° of power flows continuously transmits.
It should be noted that variable transmission refers to the transmission that can continuously obtain any transmission ratio in slewing range.
For the utility model, drive path schematic diagram is as shown in Figure 8.
It should be noted that external power through primary input axis 1101 double internal-gearing planet gear machines into commutation planet row
Then the sun gear 11 of structure passes through the output element planet row planet carrier 14 of commutation planet row Zhong Shuan internal-gearing planet gear mechanism
Output is output to the gear ring 142 of synchronized reversed planet row, then power from synchronized reversely planet row be divided into three tunnels be input to it is non-circular
Branch's transmission parts of gear mechanism.
The first via: the gear ring 142 of synchronized reversed planet row is input to the stator 144 for the phase adjusting device being attached thereto,
It is input to the first input shaft 31 again, the first input shaft 31 and the first non-circular driving gear 3 are structure as a whole, the first non-circular active
Gear 3 and the first non-circular driven gear 4 engage, and the first non-circular driven gear 4 is connected by spline with 5 spline of intermediate supports axis,
Intermediate supports axis 5 is connected by spline with box of tricks sun gear 9.
Second tunnel: the planet row planet carrier 145 of synchronized reversed planet row is transferred to the rotor 143 of phase regulator, through turning
Son 143 is transferred to the second input shaft 1201, and the second input shaft 1201 and the second non-circular driving gear 121 are structure as a whole, and second
Non-circular driving gear 121 and the second non-circular driven gear 111 engage.
Third road: the sun gear 141 of synchronized reversed planet row is transferred to the third input of non-circular gear stepless speed changing mechanism
Axis 1202, third input shaft 1202 and the non-circular driving gear 122 of third are structure as a whole, the non-circular driving gear 122 of third and
Three non-circular driven gears 112 engage.
Due to being equipped with clutch 13 between the second non-circular driven gear 111 and the non-circular driven gear 112 of third, first
Under the action of clutch 130, the second non-circular driven gear 111 and the non-circular driven gear 112 of third only one can and second in
Between axis 110 combine, another is in discrete state, i.e., the second above-mentioned road power and third road power are in first clutch 130
Under the action of be only input to the second jackshaft 110 all the way.
It is connected with one-way clutch 10 between second jackshaft 110 and differential structure, under the control of one-way clutch 10,3
Box of tricks planet carrier 8 connects in 110 continuous relay of jackshaft and 3 branch's running parts of a branch's running part.Appoint
One-way clutch 10 in only one branch of one moment is in bonding state, allows the second jackshaft 110 and differential of this branch
Mechanism planet carrier 8 connects, and realizes the power cycle transmitting of three branches.
Power divides two-way to be input to box of tricks from the sun gear 9 and box of tricks planet carrier 8 of box of tricks, then by difference
The output element box of tricks gear ring 7 of fast mechanism exports, and output element box of tricks gear ring 7 and 61 spline of intermediate connecting shaft connect
It connects, intermediate connecting shaft 61 and cylinder driving gear 6 are connected, and cylinder driven gear 6 and cylinder driven gear 2 engage, and cylinder is driven
It is key connection between gear 2 and main output shaft 21, main output shaft 21 is connected with more gear auxiliary transmissions.
For the utility model, non-circular gear stepless speed changing mechanism and auxiliary transmission group based on adder principle are utilized
The mode of conjunction realizes segmentation variable transmission, and the transmission ratio variation range schematic diagram of non-circular gear stepless speed changing mechanism is as schemed
Shown in 9；The stepless schematic diagram of the segmentation of resultant gear ratio is as shown in Figure 10.
For the speed regulation process of description segmentation variable speed, it is classified as following two stages:
One, the first stage.Non-circular gear stepless speed changing mechanism relies on phase regulator, by adjusting the first non-circular driving tooth
The first non-circular gear pair and the second non-circular driving gear 121 and second that wheel 3 and the first non-circular driven gear 4 form are non-circular
The phase relation between the second non-circular gear pair that driven gear 111 forms completes variable ratio transmission (at this point, the non-circular master of third
Moving gear 122 and the non-circular driven gear 112 of third are in idling conditions).Speed ratio variation range is A~B, is had: B=Aq.
That is: transmission ratio is gradually increased by extreme value A, and when the phase of adjusting reaches 130 ° of peak value, this section of transmission ratio reaches maximum value B, this rank
The more gear auxiliary transmissions of section are direct gear, and total transmission ratio that exports is A~B.
Under the action of first clutch 130, the second non-circular driving gear 121 and the second non-circular driven gear 111 are separated
Start to dally, the non-circular driving gear 122 of third and the non-circular driven gear 112 of third engage, because of the second non-circular driving gear 121
The non-circular gear pair formed with the second non-circular driven gear 111, with the non-circular driving gear 122 of third and the non-circular driven gear of third
Phase difference between the non-circular gear pair of 112 compositions is 130 °, and coaxial counter motion, therefore at this point, the non-circular driving tooth of third
The position for the non-circular gear pair that wheel 122 and the non-circular driven gear 112 of third form and the second non-circular driving gear 121 and second are non-
The non-circular gear that circle driven gear 111 forms is identical to position in the initial state, i.e., transmission ratio is returned to from an extreme value at this time
Another extreme value, it may be assumed that A is returned to by B.
Two, second stage.Phase regulator is continued to adjust in the opposite direction, the transmission of non-circular gear stepless speed changing mechanism
Than continuing to increase, and increase mode is identical with the first stage, i.e., speed ratio increases to B by A, while more gear auxiliary transmissions are connected into
Next gear (being equivalent on the basis of existing transmission ratio multiplied by q), it is Aq~Bq that this stage, which always exports transmission ratio, it may be assumed that B~Bq,
So the minimum value that the stage always exports transmission ratio is equal with the total output maximum value of transmission ratio of stage one, two stage nothing is completed
Grade speed change.
The process of duplication stages one Yu stage two, Zhou Erfu are only needed to continue to increase transmission ratio for the utility model
Begin, 2 can be connected to from a gear by n planet row more gear auxiliary transmissions in seriesnGear completes segmentation (2nSection) variable speed.
Input speed is n in the utility modelin, output revolving speed is nout, the first non-circular gear to 3/4 the driving and driven gear teeth
Number is respectively z3, z4, and the second non-circular gear is respectively z to 12/11 driving and driven tooth number12、z11, the first non-circular driving gear
3 revolving speed is n3, the revolving speed of the second non-circular driving gear 121 and the non-circular driving gear 122 of third is n12, box of tricks sun gear
9 revolving speed is ns, the revolving speed of box of tricks planet carrier 8 is nH, the revolving speed of box of tricks gear ring 7 is nR, then n3=n12=ni, nR=nout.Double internal messing planet differential mechanism characteristics parameter values are k, are transported by double internal messing planet differentials mechanism
Dynamic characteristic equation ns+(k-1)nH-knR=0, it can obtain:
That is:
ω4It is the first non-circular gear to transmission ratio inverse, ω11It is the second non-circular gear to transmission ratio inverse, r4And r11Point
Not Wei the first and second non-circular gears to the average value of transmission ratio inverse, As shown in figure 11, ω4With
ω11It is linear change, s within the scope of 0 °~260 °4And s11Respectively the first and second non-circular gears are to transmission ratio inverse figure
As linearity range amplitude, then its transmission ratio function is respectively as follows:
ω4And ω11It is non-linear section within the scope of 260 °~360 °, it can not to avoid the pitch curve of non-circular gear from existing
It leads a little, using sinusoidal (cosine) curve within the scope of 260 °~360 °, as shown in figure 12.To connect non-circular gear pitch curve cover
It is continuous, polar diameter is unlikely too small, usually take r4=r11=1, due to initial position phase difference be 0 ° when, have perseverance within the scope of 0 °~260 °
Fixed resultant gear ratio, is denoted as i0, distinguishingly, take t=0,130 °, 260 °, then
Then,
If ω4Opposite ω11It moves to left and is negative, moves to right and be positive, and -130≤t4-t11≤ 130, then
Due to s4< 1 is permanent to be set up, so the gear range of the utility model non-circular gear stepless speed changing mechanism are as follows:
As long as that is, given box of tricks characteristic ginseng value k and ω11Linearity range amplitude s11, corresponding transmission ratio can be obtained
Range.
For the versatility of enhancing gear and its process tool, keep the shape of two non-circular gears pair just the same, this is practical
Box of tricks characteristic ginseng value k=2 is taken in novel embodiment.To enhance the machinability of non-circular gear and the shape of pitch curve, lead to
Normal ω4Linearity range amplitude s4< 0.5 and the smaller the better.So the maximum value of this non-circular gear stepless speed changing mechanism transmission ratio i
Range is imax∈ [4/5,4/3], i.e. s4When=0.5.As it can be seen that gear range very little, to expand gear range, this is practical
The novel addition after non-circular gear stepless speed changing mechanism expands ratio coverage by the auxiliary transmission that multiple planet rows form.
In the example of the utility model, taking auxiliary transmission planet number of rows is 4, k=2, s11=0.36, then i ∈ [0.847,
1.18], the variation of transmission ratio is bent when the transmission ratio inverse of corresponding two non-circular gear pair, limit phase difference and out of phase difference
Line, as shown in Figure 12~Figure 15.
It should be noted that abscissa is the phase difference of the first and second non-circular gears pair in Fig. 9, ordinate is not
When cooperation keeps off auxiliary transmission more, the gear range of non-circular gear stepless speed changing mechanism, A represents non-circular gear stepless speed changer
The minimum value of structure transmission ratio, B representative are the maximum values of non-circular gear stepless speed changing mechanism transmission ratio.In Figure 10, A represents non-circular
The minimum value of gear stepless variable drive structure transmission ratio, abscissa are the gears of more gear auxiliary transmissions, and ordinate is that the more gears of cooperation are secondary
When speed changer, the gear range of overall setup, this figure and Figure 10 are that cooperation is for illustrating the stepless change of Combined noncircular gear
Fast transmission device realizes the principle of segmentation variable speed, so ordinate does not have specific scale.In Figure 11, abscissa right and wrong
The phase of Knucle-gear pair, that is, its angle for turning over, ordinate represent non-circular gear to the inverse of transmission ratio, ω4It is first
Non-circular gear is to transmission ratio inverse, ω11It is the second non-circular gear to transmission ratio inverse, r4And r11Respectively first and second is non-circular
The average value of gear mesh transmission ratio inverse, s4And s11Respectively the first and second non-circular gears are to transmission ratio inverse image linearity range
Amplitude, i0For non-circular gear stepless speed changing mechanism the first and second non-circular gears to phase difference is 0 when transmission ratio.
In addition, in Figure 12, ω4It is the first non-circular gear to transmission ratio inverse, ω11It is the second non-circular gear to transmission ratio
It is reciprocal.In Figure 13, ω4It is the first non-circular gear to transmission ratio inverse, ω11It is the second non-circular gear to transmission ratio inverse.?
In Figure 14, ω4It is the first non-circular gear to transmission ratio inverse, ω11It is the second non-circular gear to transmission ratio inverse.In Figure 15,
Abscissa is the gear of more gear auxiliary transmissions, when ordinate is that cooperation keeps off auxiliary transmission more, the gear range of overall setup.
According to multiple-limb non-circular gear drive principle and box of tricks kinetic characteristic equation, it is found that the transmission of Figure 13
The Power flow of one-way clutch is not met than changing, and Figure 14 is conformed exactly to, i.e., actually used gear range
For i ∈ [0.847,1].Here taking the common ratio between auxiliary transmission various gears is 1.166, therefore the resultant gear ratio of target model machine is reachable
1.16615=10.011, variation range is as shown in figure 15, this transmission ratio be all it is positive, be suitable for forward gear.By the utility model
Middle commutation planet row transmission ratio value is -1, then the negative transmission ratio of co-extensive can be achieved, suitable for reversing gear.
In conclusion compared with prior art, a kind of novel combination type non-circular gear provided by the utility model is stepless
Variable speed drive can reliably eliminate power cycle problem present in non-circular gear shifting mechanism, increase transmission effect
Rate guarantees there is good transmission performance, is conducive to widely promote and apply, be of great practical significance.
The above is only the preferred embodiment of the utility model, it is noted that for the common skill of the art
For art personnel, without departing from the principle of this utility model, several improvements and modifications can also be made, these improve and
Retouching also should be regarded as the protection scope of the utility model.
Claims (10)
1. a kind of novel combination type non-circular gear infinitely variable speed transmission characterized by comprising be mutually connected one
A commutation planet row (100) rising, a phase regulator (200), a synchronized reversed planet row, a non-circular gear are total to
With input and output transmission mechanism and three groups of non-circular gear branch transmission mechanisms.
2. novel combination type non-circular gear infinitely variable speed transmission as described in claim 1, which is characterized in that the commutation
Planet row (100) includes planet row sun gear (11), planet row shell (12), planet row gear ring (13), planet row clutch collar
(16), left-end components (1601), primary input axis (1101), planet row planet carrier (14) and planet row ring gear (17)；
Inside gear teeth meshing of the planet row sun gear (11) by the gear teeth and planet row ring gear (17) on the outside of it, planet row ring gear
(17) it is connected with planet row planet carrier (14), the gear teeth meshing of the gear teeth and planet row gear ring (13) on the outside of planet row ring gear (17)；
Planet row sun gear (11) left end is connected with and its integrally formed primary input axis (1101)；
It is equipped with endless v slot on the right side of left-end components (1601) outer end, is key between inner end and primary input axis (1101) outer end
Connection；
Outer end portion is equipped with endless v slot on the right side of planet row clutch collar (16), is used for and the endless v on the left of the shell (12)
Slot combines.
3. novel combination type non-circular gear infinitely variable speed transmission as described in claim 1, which is characterized in that described non-circular
It includes: that the first non-circular driving gear (3), the second non-circular driving gear (121), third are non-that gear, which shares input and output transmission mechanism,
Circle driving gear (122) and cylinder driven gear (2)；
First input shaft (31) an of horizontal distribution is fixedly installed on the left of the first non-circular driving gear (3)；
The second input shaft (1201) are fixedly installed on the left of the second non-circular driving gear (121)；
Third input shaft (1202) are fixedly installed on the left of the non-circular driving gear of third (122)；
The third input shaft (1202) is inserted into second input shaft (1201), the second input shaft (1201) insertion
Into first input shaft (31)；
Main output shaft (21) are fixedly installed on the right side of the cylinder driven gear (2).
4. novel combination type non-circular gear infinitely variable speed transmission as claimed in claim 3, which is characterized in that described in every group
Non-circular gear branch transmission mechanism include: the first non-circular driven gear (4), the second non-circular driven gear (111), third it is non-circular from
Moving gear (112) and cylinder driving gear (6), in which:
The first non-circular driven gear (4) is intermeshed with the described first non-circular driving gear (3), and the two composition first is non-circular
Gear mesh；
The second non-circular driven gear (111) is intermeshed with the described second non-circular driving gear (121), the two composition second
Non-circular gear pair；
The non-circular driven gear of third (112) and the non-circular driving gear of the third (122) are intermeshed, the two composition first
Non-circular gear pair；
The cylinder driving gear (6) and the cylinder driven gear (2) are intermeshed；
It extends transversely through in the second non-circular driven gear (111) and the non-circular driven gear of third (112) through the second jackshaft
(110)；
The first intermediate connecting shaft (61) are fixedly installed on the left of the cylinder driving gear (6)；
The first non-circular driven gear (4), the second non-circular driven gear (111), the non-circular driven gear of third (112) and cylinder
It is extended transversely through in driving gear (6) and is provided with an intermediate supports axis (5), and the intermediate supports axis (5) is turned left successively from the right side
Extend through the first intermediate connecting shaft (61) and the second jackshaft (110).
5. novel combination type non-circular gear infinitely variable speed transmission as claimed in claim 4, which is characterized in that described second
First clutch (130) are provided between non-circular driven gear (111) and the non-circular driven gear of third (112), the third is non-
A box of tricks is provided between circle driven gear (112) and the cylinder driving gear (6).
6. novel combination type non-circular gear infinitely variable speed transmission as claimed in claim 5, which is characterized in that described second
An one-way clutch (10) is additionally provided between jackshaft (110) and box of tricks planet carrier (8).
7. novel combination type non-circular gear infinitely variable speed transmission as claimed in claim 5, which is characterized in that the differential
Mechanism includes box of tricks gear ring (7), box of tricks planet carrier (8) and box of tricks sun gear (9).
8. novel combination type non-circular gear infinitely variable speed transmission as claimed in claim 7, which is characterized in that described first
Input shaft (31) and the first non-circular driving gear (3) are structure as a whole, and the first non-circular driven gear (4) is by spline in
Between support shaft (5) be connected, the intermediate supports axis (5) passes through box of tricks sun gear (9) phase in spline and box of tricks
Even；
Second jackshaft (110) is connected by one-way clutch (10) and box of tricks planet carrier (8)；
130 ° of phase phase difference of second non-circular driving gear (121) and the non-circular driving gear of third (122)；
It is structure as a whole between the cylinder driven gear (2) and main output shaft (21).
9. the novel combination type non-circular gear infinitely variable speed transmission as described in any one of claim 4 to 8, feature exist
In the phase regulator (200) is made of stator (144) and rotor (143)；
The synchronized reversed planet row is using double internal-gearing planet gear mechanisms, the sun gear including synchronized reversed planet row
(141), the planet carrier (145) of the gear ring (142) of synchronized reversed planet row and synchronized reversed planet row；
It is key connection between the gear ring (142) and the stator (144) of the synchronized reversed planet row；
The stator (144) and the first input shaft (31) are key connection；
It is key connection between the synchronized reversed planet row planet carrier (145) and the rotor (143)；
It is key connection between the rotor (143) and the second input shaft (1201)；
It is key connection between the synchronized reversed planet row sun gear (141) and third input shaft (1202).
10. the novel combination type non-circular gear infinitely variable speed transmission as described in any one of claim 3 to 8, feature
It is, further includes at least one auxiliary transmission (300), the auxiliary transmission (300) is connected with the main output shaft (21)；
Second input shaft (1201) and the second non-circular driving gear (121) are an integral molding structure, the third input shaft
(1202) it is an integral molding structure with the non-circular driving gear of third (122).
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108412982A (en) * | 2018-05-11 | 2018-08-17 | 中国人民解放军陆军军事交通学院 | A kind of novel combination type non-circular gear infinitely variable speed transmission |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108412982A (en) * | 2018-05-11 | 2018-08-17 | 中国人民解放军陆军军事交通学院 | A kind of novel combination type non-circular gear infinitely variable speed transmission |
| CN108412982B (en) * | 2018-05-11 | 2024-01-26 | 中国人民解放军陆军军事交通学院 | Combined non-circular gear stepless speed change transmission device |
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