CN207005216U - Mechanical gear formula ST - Google Patents
Mechanical gear formula ST Download PDFInfo
- Publication number
- CN207005216U CN207005216U CN201720986690.1U CN201720986690U CN207005216U CN 207005216 U CN207005216 U CN 207005216U CN 201720986690 U CN201720986690 U CN 201720986690U CN 207005216 U CN207005216 U CN 207005216U
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- CN
- China
- Prior art keywords
- gear
- sun
- planet carrier
- ring
- output
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Abstract
The utility model discloses a kind of mechanical gear formula ST, including input shaft, output shaft, it is arranged on the first planet row of enclosure interior, second planet row and differential gear system, the gear ring engaged transmission of input shaft and the first planet row, second planet row and the first planet row share gear ring and planet carrier, and second sun gear the number of teeth be more than the first sun gear the number of teeth, first sun gear gives power transmission to differential gear system, the output shaft of differential gear system is connected with gearshift component and transmits power to output shaft, it is connected simultaneously with second sun, second sun gear and planet carrier can only one-directional rotations, and second sun gear steering it is opposite with gear ring, the steering of planet carrier is identical with gear ring.The utility model realizes the stepless gear shift of gearratio by the first planet row, the second planet row and differential gear system, possesses continuity, the ride comfort of existing CVT speed changers in overall process, while has MT speed changer booster responses fast, the characteristics of bearing big moment of torsion.
Description
Technical field
The utility model belongs to drive technology field, more particularly to a kind of mechanical gear formula ST.
Background technology
With the fast development of auto industry, the fast development of associated vehicle parts industry is brought, with automobile industry political affairs
Plan, requirement to the driver comfort of vehicle also more and more higher more and more with the people of car, therefore, the gear shift product to speed changer
Matter proposes higher requirement.Real-life speed changer has four kinds, is respectively：Manual transmission, automatic transmission, DVT are double
Clutch speed changer and CVT STs, and manual transmission needs manual shift and easily produces pause and transition in rhythm or melody sense, it is automatic to become
When fast device accelerates delay of response and in gear shift clutch and brake combination can produce pause and transition in rhythm or melody sense, DVT double-clutch speed changers and
It is slow that CVT STs accelerate, and CVT STs are by belt or Steel Belt Transmission, it is impossible to bears big
Moment of torsion, above-mentioned automatic transmission, DVT double-clutch speed changers, CVT STs are to control to pass by electronic circuit system
The change of dynamic ratio, thus when suddenly accelerating not as MT speed changers it is corresponding directly, engine has the power loss of idle running.
Utility model content
The purpose of this utility model is overcome the deficiencies in the prior art and to provide a kind of booster response fast, can bear big
Moment of torsion, the mechanical gear formula ST of no pause and transition in rhythm or melody sense.
In order to solve the above technical problems, mechanical gear formula ST provided by the utility model, including shell
Body, the input shaft and output shaft being sleeved on housing, in addition to be arranged on the first planet row of enclosure interior, the second planet row and
Differential gear system, first planet row include the first gear ring, multiple first planetary gears, the first row with input shaft engaged transmission
Carrier and the first sun gear, first planetary gear can rotation be arranged on the first planet carrier on and respectively with first tooth
The external tooth of the internal tooth of circle and the first sun gear often engages, the second described planet row include the second gear ring, multiple second planetary gears,
Second planet carrier and the second sun gear, the second described planetary gear can rotation be arranged on the second planet carrier and respectively with the
The external tooth of the internal tooth of two gear rings and the second sun gear often engages, wherein the first described gear ring and the second gear ring are same gear ring,
The first described planet carrier and the second planet carrier are same planet carrier, the first described sun gear can rotation, described second too
Sun wheel by unilateral bearing limit its can only one-directional rotation and rotation direction it is opposite with gear ring steering or do not turn, described the first row
Carrier by another unilateral bearing limit its can only one-directional rotation and rotation direction it is identical with gear ring steering or do not turn, described
The number of teeth of one sun gear is less than the number of teeth of the second described sun gear；
Described differential gear system include be connected with the first sun gear coaxial transmission driving side gear, driven side gear,
The first gear and second gear that are arranged side by side, often engage with driving side gear in first gear and can rotation it is multiple
First bevel gear, in second gear and can rotation multiple second bevel gears and duplicate gear, described first cone tooth
The axis of wheel is vertical with the axis of first gear, and the axis of described second bevel gear and the axis of described second gear hang down
Directly, it is provided with two-sided side gear between described first gear and second gear, the two-sided side gear one side and described the
One bevel gear often engages, and another side often engages with described second bevel gear, the double-face side Gear axis and first tooth
Wheel axis overlap, described duplicate gear rotatably be arranged on housing in and respectively with described first gear and second gear
Often engagement, described second bevel gear is often engaged with described driven side gear and outputed power, on described driven side gear
It is coaxial to be fixed with the 3rd gear, be provided with described housing the 4th gear that is often engaged with the 3rd described gear and with it is described
The 4th gear coaxial transmission connection the 5th gear；
Power from driving side gear successively through first bevel gear, two-sided side gear, second bevel gear gearratio with successively
Gearratio through first bevel gear, first gear, duplicate gear, second gear, second bevel gear differs；
Also include gearshift component, the gearshift component includes being fixedly and coaxially connected external splines on output shaft, is set in
It is on external splines and being capable of internal spline sliding sleeve, the first output gear and the second output gear positioned at external splines both sides in axial sliding
Take turns, the slide-bar to match with the internal spline sliding sleeve is equipped with described the first output gear and the second output gear；
Transmission axle is coaxially fixed with the second described sun gear, be fixed with described transmission axle the 6th gear and
7th gear, the 3rd described gear pass sequentially through the 4th gear and transmit power to the 5th gear, the 5th described gear point
Often not engaged with described the first output gear and the 6th gear, the 7th described gear often engages with the second output gear, when
When internal spline sliding sleeve is combined with the first output gear, external splines drives output shaft just to switch to forward gear；When internal spline sliding sleeve and
When two output gears combine, external splines drives output shaft to be reversed to reverse gear.
Compared with prior art, the utility model has the advantages that：The utility model mechanical gear formula is stepless certainly
Dynamic speed changer combine MT speed changers and CVT speed changers the advantages of, booster response is fast, can bear big moment of torsion, no pause and transition in rhythm or melody sense,
Gearratio pace of change is fast, and cost is low.
Brief description of the drawings
Fig. 1 is structural representation of the present utility model.
Embodiment
The utility model is further described below in conjunction with the drawings and specific embodiments.
Referring to Fig. 1, ST provided by the utility model, including housing, the input that is sleeved on housing
Axle 1 and output shaft 2, in addition to it is arranged on the first planet row, the second planet row and differential gear system of enclosure interior, the first planet
Row includes the first gear ring 3, multiple first planetary gears 4, the first planet carrier 5 and the first sun gear 6, is fixedly connected with output shaft 1
First input gear 7, suit is fixed with the second input gear 8 often engaged with the first input gear 7 outside the first gear ring 3, and first
Planetary gear 4 can rotation be arranged on the first planet carrier 5 and it is outer with the internal tooth of the first gear ring 3 and the first sun gear 6 respectively
Tooth often engages, and the second planet row includes the second gear ring, multiple second planetary gears 9, the second planet carrier and the second sun gear 10, and second
Planetary gear 9 can rotation be arranged on the second planet carrier on and respectively with the internal tooth of the second gear ring and the external tooth of the second sun gear 10
Often engagement, wherein the first gear ring 3 and the second gear ring are same gear ring, the first planet carrier 5 and the second planet carrier are same planet carrier,
First sun gear 6 can rotation, the second sun gear 10 limits it by the first unilateral bearing 11 and one-directional rotation and can only turn to and the
One gear ring 3 is turned to opposite or not turned, the first planet carrier 5 by the second unilateral bearing 12 limit its can only one-directional rotation and turn to
First gear ring 3 is turned to identical or not turned, and the number of teeth of the first sun gear 6 is less than the number of teeth of the second described sun gear 10；Differential tooth
Train includes driving side gear 13, driven side gear 14, the first tooth being arranged side by side being connected with the coaxial transmission of the first sun gear 6
Wheel 15 and second gear 16, in first gear 15 with driving side gear 13 often engage and can rotation it is multiple first bore teeth
Wheel 17, in second gear 16 and can rotation multiple second bevel gears 18 and duplicate gear 19, first bevel gear 17
Axis is vertical with the axis of first gear 15, and the axis of second bevel gear 18 is vertical with the axis of second gear 16, in the first tooth
Two-sided side gear 20, axis and the first gear 15 of two-sided side gear 20 are provided between wheel 15 and second gear 16 in housing
Axis overlap, the two-sided one side of side gear 20 often engages with first bevel gear 17, and another side often engages with second bevel gear 18,
Duplicate gear 19 is rotatably arranged in housing and often engaged with first gear 15 and second gear 16 respectively, second bevel gear
18 often engage with driven side gear 14 and output power, and the 3rd gear 21 are coaxially fixed with driven side gear 14, in housing
It is interior to be provided with and the 3rd the 4th gear 22 often engaged of gear 21 and the 5th gear 23 being connected with the coaxial transmission of the 4th gear 22；The
The axis coinciding of one gear 15 and second gear 16；
Power from driving the transmission through first bevel gear 17, two-sided side gear 20, second bevel gear 18 successively of side gear 13
Than more than the transmission through first bevel gear 17, first gear 15, duplicate gear 19, second gear 16, second bevel gear 18 successively
Than；
Also include the gearshift component being arranged in housing, gearshift component includes being fixedly and coaxially connected outer on output shaft 2
Spline 24, the internal spline sliding sleeve 25 being set on external splines 24, the first output gear 26 and second positioned at the both sides of external splines 24
The slide-bar to match with internal spline sliding sleeve 25 is equipped with output gear 27, the first output gear 26 and the second output gear 27
28；
Transmission axle 29 is coaxially fixed with second sun gear 10, the 6th gear 30 and are fixed with transmission axle 29
Seven gears 31, the 3rd gear 21 pass sequentially through the 4th gear 22 and transmit power to the 5th gear 23, the 5th gear 23 respectively with
First output gear 26 and the 6th gear 30 often engage, and the 7th gear 31 often engages with the second output gear 27, when internal spline is slided
When set 25 is combined with the first output gear 26, external splines 24 drives output shaft 2 just to switch to forward gear；When internal spline sliding sleeve 25 and
When two output gears 27 combine, external splines 24 drives output shaft 2 to be reversed to reverse gear.
Operation principle of the present utility model is：
According to law of conservation of energy, the characteristic equation of the simple planetary arrangement characteristics of motion is：n1+an2-(1+a)n3=
0, wherein n1For sun wheel speed；n2For gear ring rotating speed；n3Planet carrier rotating speed.In the first planet row and the second planet row n2It is identical,
When the second planet row sun gear number of teeth is more than the first planet row sun gear number of teeth, if the first sun gear, the second sun gear do not turn,
Simultaneously driven gear ring, then the first planet carrier rotating speed be more than the second planet carrier rotating speed；If the first planet carrier, the second planet carrier are not
Turn, while driven gear ring, then the first sun wheel speed is more than the second sun wheel speed.According to this transmission design, the first planet
Row and the second planet row share gear ring and planet carrier, the second sun gear 10 and can not rotate in same direction with gear ring, driven gear ring, planet carrier
Moved by the second planet row track, the first planet row sun gear must rotate backward speed discrepancy (first sun for making up planet carrier
The rotating speed of wheel 6 is consistently greater than the rotating speed of the second sun gear 10), if planet carrier does not turn, driven gear ring, now the first sun gear 6 with
The rotating ratio of second sun gear 10 is minimum, and the rotating ratio of gear ring and output sun gear (the second sun gear) is minimum, and therefore, first too
Sun wheel is 6 small with the rotating ratio of the second sun gear 10, and gear ring is with exporting the rotating ratio of sun gear (the second sun gear) with regard to small, accordingly
, the rotating ratio of the first sun gear 6 and the second sun gear 10 is big, and gear ring is with exporting the rotating ratio of sun gear (the second sun gear) just
Greatly.
First sun gear 6 and the change of the rotating ratio of the second sun gear 10 and gear ring and output sun gear rotating ratio change are present pair
It should be related to, the former rotating ratio excursion is small, and the latter's rotating ratio excursion is big, that is to say, that the first planet row and the second row
Star row shares gear ring and planet carrier combination, inputs the first sun gear 6 and the minizone rotating ratio of the second sun gear 10, corresponding output gear
Circle and the big section rotating ratio of output sun gear (the second sun gear), automotive transmission maximum transmission ratio is 5 at present:1 or so, input
To output, gear ring and output sun gear gearratio 5:The gearratio of 1 corresponding first sun gear 6 and the second sun gear 10 is 1.2:1
Left and right, the first sun gear 6 and the rotating ratio of the second sun gear 10 diminish, and planet carrier rotating speed diminishes, gear ring and output sun gear transmission
Than diminishing, (1.042 during 10 rotating ratio minimum of the first sun gear 6 and the second sun gear：1 or so), planet carrier does not turn, gear ring with it is defeated
Sunny wheel gearratio is minimum, therefore the first sun gear 6 and the rotating ratio section of the second sun gear 10 are 1.2:1-1.042:1 it
Between, the first sun gear 6 and the change of the rotating ratio of the second sun gear 10 are completed by differential speed gears.
For the synchronization of gear ring in the rotating speed of engine, the rotating speed of planet carrier depends on the rotating speed of the second sun gear 10, the
The rotating speed of two sun gear 10 is slow, then planet carrier rotating speed is fast, otherwise the rotating speed of the second sun gear 10 is fast, then planet carrier rotating speed is slow, and first too
The rotating speed of sun wheel 6 depends on the rotating speed of planet carrier, and planet carrier rotating speed is fast, then the rotating speed of the first sun gear 6 is slow, and planet carrier rotating speed is slow,
Then the rotating speed of the first sun gear 6 is fast.Differential gear system automatic speed governing device, power are exported to driving side gear by the first sun gear 6
13, power is reached the second sun gear 10 and output shaft 2 by driving side gear 13 by the drive lines of two different drive ratios, and two
The different drive line of bar gearratio corresponds to the maximum transmission ratio (1.2 of the first sun gear 6 and the second sun gear 10 respectively:1) and
Fastest ratio (1.042:1), due to power from driving side gear 13 successively through first bevel gear 17, two-sided side gear 20, the
The gearratio of two bevel gears 18 (circuit A) is more than successively through first bevel gear 17, first gear 15, duplicate gear 19, the second tooth
Wheel 16, the gearratio of second bevel gear 18 (circuit B), i.e. A circuits are laborsaving transmission, according to lever principle, A route lever thick stick fulcrums
For first gear 15 and second gear 16, B circuits balance pivot is two-sided side gear 20, when vehicle starting, power input to
Side gear 13 is driven, because A circuits are laborsaving transmission, power is driven through the driven sun gear of side gear 14 to the second 10 by A circuits
And export, now A circuits fulcrum first gear 15 and second gear 16 do not turn, and the two-sided side gear 20 of B circuit fulcrums rotates, if
Power enough and vehicle is produced inertia, it is necessary to driving force when being less than B circuit power, B circuits follow up, A circuit balance pivots
Rotating, B circuit fulcrum rotating speeds are slack-off, and A circuits and B circuit fulcrums change, and continue input power and walk the transmission of A circuits, by
Rotated in A circuit fulcrums, now A circuits gearratio is less than rotation ratio when fulcrum does not turn, and gearratio diminishes, continues to drive therewith
Motor-car, under inertia force effect, B circuits follow up again, and A circuit fulcrum rotating speeds accelerate, and A circuit gearratios diminish again, car
Accelerate to carry out above-mentioned steps circulation successively, when vehicle drives to certain speed, power from A circuits input when, power and resistance
When reaching balance, now car speed is not further added by, and B lines can not follow up, and A line fulcrums do not change, and gearratio no longer occurs
Change, vehicle at the uniform velocity travel.When vehicle driving up or resistance become it is big when, slack-off with speed, B circuit rotating speeds are slack-off, and A circuits pass
Dynamic than becoming big, if speed continuation is slack-off, B circuit rotating speeds are slack-off again, and A circuit gearratios continue to become big.The change of A circuit gearratios
Change, depending on the change (fulcrum turns slowly, then gearratio is big, and fulcrum turns soon, then gearratio is small) of A line bar thick stick fulcrums, A circuits
(B circuit rotating speeds are slow, and A circuit fulcrum rotating speeds are slow, otherwise B circuit rotating speeds for the rotation speed change for changing and depending on B circuits of fulcrum
Hurry up, A circuit fulcrum rotating speeds are fast), the change of B circuit rotating speeds depends on the size of the inertia force of vehicle again, and the size of inertia force takes
Certainly in outside vehicle resistance and driving force size, driving force depends on engine power and compares size with transmission.
When vehicle band shelves slide, because in reaction force state, B lines are laborsaving transmissions, under inertia force effect, the
Two sun gears 10 are driven through the B circuits in differential gear system and the first sun gear 6, now the first sun gear 6 and the second sun gear
10 wheel gearratios are minimum, and B line fulcrums do not turn, and planet carrier is lived by unidirectional bearing lock and is in the state that stops operating.Add again after sliding
When fast, planet carrier rotates in same direction with gear ring, and power drives to second too from the first sun gear 6 through the A circuits in differential gear system
Sun wheel 10 and output shaft 2, A circuits fulcrum influence B circuits with speed size and produce corresponding gearratio.
In a word, the utility model mechanical gear formula ST, there is fast booster response, smooth gear shifting, can hold
The characteristics of by big torque output, there is the value of popularization and application.
The preferred embodiment of the utility model creation is the foregoing is only, is not created to limit the utility model
Make, within all spirit and principle created in the utility model, any modification, equivalent substitution and improvements made etc., all should include
Within the protection domain that the utility model is created.
Claims (1)
1. a kind of mechanical gear formula ST, including housing, the input shaft and output shaft that are sleeved on housing, it is special
Sign is：Also include the first planet row, the second planet row and differential gear system for being arranged on enclosure interior, first planet row
Including the first gear ring with input shaft engaged transmission, multiple first planetary gears, the first planet carrier and the first sun gear, described first
Planetary gear can rotation be arranged on the first planet carrier and it is outer with the internal tooth of first gear ring and the first sun gear respectively
Tooth often engages, and the second described planet row includes the second gear ring, multiple second planetary gears, the second planet carrier and the second sun gear,
The second described planetary gear can rotation be arranged on the second planet carrier and the internal tooth and second sun with the second gear ring respectively
The external tooth of wheel often engages, wherein the first described gear ring and the second gear ring are same gear ring, the first described planet carrier and second
Planet carrier is same planet carrier, the first described sun gear can rotation, the second described sun gear limits it by unilateral bearing
Can only one-directional rotation and rotation direction turned to gear ring on the contrary, the first described planet carrier limits it by another unilateral bearing
Can one-directional rotation and rotation direction it is identical with gear ring steering or do not turn, the number of teeth of the first described sun gear is less than described second
The number of teeth of sun gear；
Described differential gear system includes driving side gear, the driven side gear, side by side being connected with the first sun gear coaxial transmission
The first gear and second gear of setting, in first gear with driving side gear often engage and can rotation multiple first
Bevel gear, in second gear and can rotation multiple second bevel gears and duplicate gear, described first bevel gear
Axis is vertical with the axis of first gear, and the axis of described second bevel gear is vertical with the axis of described second gear,
Two-sided side gear, the two-sided side gear one side and the first described cone tooth are provided between described first gear and second gear
Wheel often engagement, another side often engages with described second bevel gear, described duplicate gear be rotatably arranged on housing it is interior and
Often engaged with described first gear and second gear respectively, described second bevel gear often engages with described driven side gear
Output power, be coaxially fixed with the 3rd gear on described driven side gear, be provided with described housing and described the
The 4th gear that three gears often engage and the 5th gear being connected with the 4th described gear coaxial transmission；
Power from driving side gear successively through first bevel gear, two-sided side gear, second bevel gear gearratio with successively through the
One bevel gear, first gear, duplicate gear, second gear, the gearratio of second bevel gear differ；
Also include gearshift component, the external splines that the gearshift component includes being fixedly and coaxially connected on output shaft is set in external splines
It is upper and can internal spline sliding sleeve, the first output gear and the second output gear positioned at external splines both sides in axial sliding, it is described
The first output gear and the second output gear on be equipped with the slide-bar to match with the internal spline sliding sleeve；
Transmission axle is coaxially fixed with the second described sun gear, the 6th gear and the 7th are fixed with described transmission axle
Gear, the 3rd described gear pass sequentially through the 4th gear and transmit power to the 5th gear, the 5th described gear respectively with
Described the first output gear and the 6th gear often engages, and the 7th described gear often engages with the second output gear, when interior flower
When key sliding sleeve is combined with the first output gear, external splines drives output shaft just to switch to forward gear；When internal spline sliding sleeve and second defeated
When going out gear combination, external splines drives output shaft to be reversed to reverse gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720986690.1U CN207005216U (en) | 2017-08-08 | 2017-08-08 | Mechanical gear formula ST |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720986690.1U CN207005216U (en) | 2017-08-08 | 2017-08-08 | Mechanical gear formula ST |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN207005216U true CN207005216U (en) | 2018-02-13 |
Family
ID=61458077
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201720986690.1U Expired - Fee Related CN207005216U (en) | 2017-08-08 | 2017-08-08 | Mechanical gear formula ST |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN207005216U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110033692A (en) * | 2019-04-28 | 2019-07-19 | 重庆理工大学 | A kind of planetary gear mechanism movement instructional device |
-
2017
- 2017-08-08 CN CN201720986690.1U patent/CN207005216U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110033692A (en) * | 2019-04-28 | 2019-07-19 | 重庆理工大学 | A kind of planetary gear mechanism movement instructional device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180213 Termination date: 20210808 |
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| CF01 | Termination of patent right due to non-payment of annual fee |