CN109442009A - A kind of variable transmission mechanism and in-wheel driving are mechanical - Google Patents
A kind of variable transmission mechanism and in-wheel driving are mechanical Download PDFInfo
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- CN109442009A CN109442009A CN201811563746.8A CN201811563746A CN109442009A CN 109442009 A CN109442009 A CN 109442009A CN 201811563746 A CN201811563746 A CN 201811563746A CN 109442009 A CN109442009 A CN 109442009A
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- gear
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- transmission mechanism
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- 230000007246 mechanism Effects 0.000 title claims abstract description 60
- 230000005540 biological transmission Effects 0.000 title claims abstract description 51
- 230000008859 change Effects 0.000 claims abstract description 11
- 238000000034 method Methods 0.000 abstract description 13
- 230000008569 process Effects 0.000 abstract description 7
- 230000009347 mechanical transmission Effects 0.000 abstract description 2
- 238000006073 displacement reaction Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 3
- 230000002411 adverse Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000013404 process transfer Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
本发明涉及机械传动技术领域，尤其涉及一种变速传动机构及轮式驱动机械。本发明利用双联太阳轮轴在基于不同的行星机构元件时会对共用行星架的输出产生不同速比这一特性，设置了低速和高速两个挡位。在输入轴转速保持不变的情况下，依靠双联太阳轮轴转速及转向的变化，配合以挡位的切换，便可在输出轴上实现从反向最大转速到正向最大转速的无级变速。在整个变速过程中，输出转速变化平顺，且无动力中断。
The invention relates to the technical field of mechanical transmission, in particular to a variable speed transmission mechanism and a wheel-type driving machine. The invention utilizes the characteristic that the output of the shared planet carrier will have different speed ratios when the double sun gear shaft is based on different planetary mechanism elements, and sets two gears of low speed and high speed. Under the condition that the rotational speed of the input shaft remains unchanged, depending on the change of the rotational speed and steering of the double sun gear shaft, and with the switching of gears, the output shaft can realize the stepless speed change from the reverse maximum speed to the forward maximum speed on the output shaft. . During the entire shifting process, the output speed changes smoothly without power interruption.
Description
Technical field
The present invention relates to technical field of mechanical transmission more particularly to variable transmission mechanism and in-wheel driving are mechanical.
Background technique
The characteristics of gear drive is that transmission ratio is fixed, and for the output demand for meeting equipment, generally requires to design more gear teeth
Wheel-speed regulating change box.Gear is more, and shift process is more smooth, and device efficiency plays more abundant.But gear, and to also result in structure more multiple
It is miscellaneous, operate it is more complicated, meanwhile, speed-changing gear box the shortcomings that there is also interruption of power transmission when carrying out gear switching, in low speed
The disadvantage is especially protruded when large torque stage band carries shift.
The universal mating more shift gear gearboxes of wheeled tractor at present, power more gear wheel gear is more, mostly manually
Shift type also has a small amount of power shift type.The shift process of power shift type gearbox can be automatically performed under driver command,
Instead of manual processes.Driver shifts gears as desired by manual operation or publication instruction when operation.Since gear becomes
The discontinuity of fast case speed ratio, and, relatively low gear is often selected to avoid frequent gear from switching driver, causes and sets
Standby power is difficult to utmostly play, and reduces operating efficiency；Also due to the discontinuity of speed-changing gear box speed ratio, starts
The optimum operating speed of machine and the best job parameter of tractor tend not to meet simultaneously, it will cause the increase of fuel consumption
Or the adverse effects such as decline of operation quality.
For gear shift technical field, especially to wheeled tractor gearbox, the continuous of speed ratio and power transmission is solved
Property is necessary.In view of this, in view of the above-mentioned problems, proposing that a kind of design is reasonable and the continuous dynamic of above-mentioned missing can be effectively improved
Power infinitely variable speed gearing.
Summary of the invention
It, can be in shift process transfer it is an object of the invention to propose that a kind of variable transmission mechanism and in-wheel driving are mechanical
Speed variation power transmission is continuous and steady.
To achieve this purpose, the present invention adopts the following technical scheme:
A kind of variable transmission mechanism is provided, comprising:
Duplex sun wheel shaft, is connected to driving mechanism；
First planet row, including the first sun gear, first sun gear be set in the duplex sun wheel shaft and with
The duplex sun wheel shaft transmission connection；
Second planet row, including the second sun gear, second sun gear be set in the duplex sun wheel shaft and with
The duplex sun wheel shaft transmission connection, the second planet carrier and the first planet row that second planet row is included are included
First planet carrier is connected as one；
Output shaft is fixedly connected with the first planet carrier；
Clutch is connect with input shaft and second planet row respectively；
Brake is connect with first planet row.
Preferably, the first gear ring of first planet row and the brake are sequentially connected.
Preferably, the second gear ring of second planet row is connect with the driven by clutches.
Preferably, further including the transmission mechanism being arranged between the second gear ring and clutch, transmission mechanism includes transmission
Gear, the transmission gear is coaxial with second gear ring and is fixedly connected, and second gear ring and the clutch pass through institute
State transmission mechanism transmission connection.
Preferably, the transmission mechanism further includes driving gear, driving gear and the clutch coaxial are arranged, described
Driving gear and the transmission gear are sequentially connected.
Preferably, second planet row includes planetary gear.
Preferably, first planet row further includes the first planet idle wheel and the second planet idle wheel.
Preferably, duplex sun wheel shaft one end is equipped with first sun gear and second sun gear, separately
One end passes through second gear ring and connect with driving mechanism.
It is mechanical that a kind of in-wheel driving is additionally provided in the present invention, including variable transmission mechanism described above.
Preferably, the driving mechanism is hydraulic motor.
The invention has the advantages that:
Second gear ring of the first gear ring and the second planet row based on the first planet row, duplex sun wheel shaft and output shaft it
Between can generate two different speed ratios, and two speed ratio opposite signs.Two gear rings are selected respectively and participate in transmission, and pass through institute
Transmission mechanism is stated to an appropriate speed ratio is determined between the gear ring and input shaft of the second planet row, has the present invention right respectively
Two gears of two slewing ranges being mutually linked are answered, bottom gear and top gear are claimed.Within the scope of bottom gear, output shaft revolving speed
The stepless variation from reversed maximum speed to bottom gear maximum speed can be achieved；Within the scope of top gear, output shaft revolving speed can be real
Now from bottom gear maximum speed to the top gear maximum speed i.e. stepless variation of this transmission mechanism maximum speed；And bottom gear with
Handoff procedure between top gear does not have power interruption.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of variable transmission mechanism provided in an embodiment of the present invention；
Fig. 2 is that the corresponding relationship in speed-change process provided in an embodiment of the present invention between main element and output shaft revolving speed is bent
Line chart.
In figure:
1, duplex sun wheel shaft；21, the first gear ring；22, first planet carrier；23, the first sun gear；24, the first planet is situated between
Wheel；25, the second planet idle wheel；31, the second gear ring；32, transmission gear；33, planetary gear；34, the second sun gear；4, output shaft；
5, clutch；6, brake；7, driving gear；8, the second planet carrier；9, input shaft.
Specific embodiment
To keep the technical problems solved, the adopted technical scheme and the technical effect achieved by the invention clearer, below
In conjunction with attached drawing and pass through specific embodiment to further illustrate the technical scheme of the present invention.It is understood that this place is retouched
The specific embodiment stated is used only for explaining the present invention rather than limiting the invention.It also should be noted that in order to just
Only the parts related to the present invention are shown in description, attached drawing and it is not all.
A kind of variable transmission mechanism is provided in the present embodiment, as shown in Figure 1, the variable transmission mechanism include: duplex too
Positive wheel shaft 1, the first planet row, the second planet row, output shaft 4, clutch 5 and brake 6.
The same end of duplex sun wheel shaft 1, and the first planet row and second is arranged in first planet row and the second planet row
Planet row is rotatablely connected with duplex sun wheel shaft 1, and the other end of duplex sun wheel shaft 1 is then connect with driving mechanism, driving
Mechanism is that duplex sun wheel shaft 1 provides power.Specifically, which is hydraulic motor.
Wherein, the second planet carrier 8 of the second planet row is connect with the first planet carrier 22 of the first planet row.And output shaft 4
It is then connect with the first planet row, the output power with the rotation of the first planet row.
In further concrete scheme:
First planet row includes: the first gear ring 21, first planet carrier 22, the first sun gear 23, the first planet idle wheel 24, and
Two planet idle wheels 25.
Second planet row includes: the second gear ring 31, the second planet carrier 8, planetary gear 33, the second sun gear 34.
Wherein the first planet idle wheel 24 and the second planet idle wheel 25 are arranged in first planet carrier 22, the first planet idle wheel 24
It is engaged respectively with the first sun gear 23 and the second planet idle wheel 25, the second planet idle wheel 25 is also engaged with the first gear ring 21.
Second sun gear 34 is engaged with planetary gear 33, and planetary gear 33 is also engaged with the second gear ring 31, and planetary gear 33 and row
Carrier 22 is connected by the second planet carrier 8.
Planet carrier 22 is rotatablely connected by the first planet idle wheel 24 and the first sun gear 23, first planet carrier 22 and output shaft
4 are fixedly connected, i.e. the revolving speed of planet carrier 22 is the revolving speed of output shaft 4.Second planet carrier 8 is connected as one with first planet carrier 22
Body.
Brake 6 can be sequentially connected with the first gear ring 21, i.e., brake 6 and the first gear ring 21 are combined or separated, braking
After device 6 is combined with the first gear ring 21, the first gear ring 21 is connected to body by brake 6, so that the first gear ring 21 is relative to system
Dynamic device 6 is static, at this point, driving mechanism driving duplex sun wheel shaft 1 rotates, first sun in duplex sun wheel shaft 1 is arranged in
Wheel 23 is rotated with duplex sun wheel shaft 1, and driving the first planet idle wheel 24 rotation, the first planet idle wheel 24 is arranged in planet carrier 22
On, the second sun gear 34 drives planetary gear 33 to rotate, and planet carrier 22 and the effect of planetary gear 33 rotate the second gear ring 31.
Transmission gear 32 is coaxial with the second gear ring 31 and is fixedly connected.
Input shaft 9 is separately connected engine, power mechanism and clutch, and engine is that input shaft 9 provides power, and inputs
Axis 9 then drives power mechanism driving driving mechanism work.Engine driving input shaft 9 drives power mechanism driving driving mechanism to turn
Dynamic, driving mechanism drives duplex sun wheel shaft 1 to rotate.
Specifically, the second gear ring 31 of above-mentioned second planet row is sequentially connected with transmission gear 32, and solid on clutch 5
Surely it is provided with a driving gear 7 coaxial with the clutch 5, which is fixedly connected with clutch 5, transmission gear
32 engage with driving gear 7.
As shown in Fig. 2, abscissa indicates that output revolving speed, ordinate indicate each element revolving speed in Fig. 2, wherein a indicates first
Rotation speed relation line between gear ring 21 and output shaft 4, b indicate that rotation speed relation line between the second gear ring 31 and output shaft 4, c indicate duplex too
Rotation speed relation line between positive wheel shaft 1 and output shaft 4, d indicate that rotation speed relation line between planet carrier 22 and output shaft 4, e indicate input shaft 9
With 4 rotation speed relation lines of output shaft.
It should be noted that brake 6 and clutch 5 be it is open in usual, driving mechanism is hydraulic motor, and power mechanism is
Hydraulic variable displacement pump, hydraulic motor and hydraulic variable displacement pump form closed type hydraulic system, the input shaft and input shaft 9 of the hydraulic variable displacement pump
Between be mechanically connected, rotating ratio is kept constant.
As depicted in figs. 1 and 2, above-mentioned variable transmission mechanism speed-change process is as follows:
Element direction of rotation sees from right to left according to Fig. 1, similarly hereinafter.Limited in the present embodiment set 9 direction of rotation of input shaft as
It clockwise, is clockwise negative sense.
When initial state, transmission mechanism is in bottom gear, and output 22 revolving speed of revolving speed, that is, planet carrier is zero.It brakes under this state
Device 6 is closed, and clutch 5 is opened, and the hydraulic variable displacement pump pivot angle of closed system is in middle position, and 1 revolving speed of duplex sun wheel shaft is zero, the
One planet row is in running order, and the second planet row is detached from work, and input shaft 9 rotates clockwise.
Based on aforementioned initial state, adjust hydraulic variable displacement pump pivot angle make hydraulic motor and the revolving speed of duplex sun wheel shaft 1 by
Zero gradually positive increase, according to the characteristic of the first planet row and the revolving speed of the first gear ring 21, as shown in Fig. 2, 22 turns of planet carrier
Speed is that the output revolving speed of output shaft 4 will be by zero gradually negative sense increase, until negative sense highest design value.Adjustment hydraulic pump pivot angle makes double
The revolving speed of connection sun wheel shaft 1 is gradually reduced by positive peak, and output revolving speed can be realized by negative sense peak and be reduced to zero
Process.
Based on aforementioned initial state, which is in bottom gear, and adjustment hydraulic variable displacement pump pivot angle makes duplex too
The revolving speed of positive wheel shaft 1 is by zero gradually negative sense increase；According to the characteristic of the first planet row and revolving speed (this state of the first gear ring 21
The lower revolving speed is that 0), revolving speed, that is, mechanism output revolving speed of planet carrier 22 will be by zero gradually positive increase；Meanwhile according to the second row
The characteristic of star row and the revolving speed of continually changing planet carrier 22, the revolving speed of the second gear ring 31 also will by zero it is gradually positive increase,
The rotation speed change of second gear ring 31 is transferred to clutch 5 by transmission gear 32 and driving gear 7, rubs inside and outside clutch 5
When pad revolving speed is equal, mechanism output revolving speed reaches the positive highest preset value and top gear range of bottom gear range
Minimum predetermined value, the revolving speed of duplex sun wheel shaft 1 also reach negative sense highest preset value；At this point, duplex sun wheel shaft 1 and input shaft
Speed ratio between 9 has reached a particular value, and mechanism is in the critical state for preparing to switch from bottom gear to top gear.
In aforementioned critical state, it is closed clutch 5, opens brake 6；The second planet row is in running order at this time, the
One planet is got rid of from work；Outside friction disc revolving speed is equal in it when due to closure clutch 5, therefore handoff procedure is without impact；Simultaneously
Brake 6 is opened due to being first closed after clutch 5 when switching, therefore handoff procedure power failure-free.
In top gear state, adjust hydraulic variable displacement pump pivot angle make the revolving speed of duplex sun wheel shaft 1 by negative sense peak by
Step is reduced to zero, then is stepped up by zero to positive peak；It is passed to according to the characteristic of the second planet row and by input shaft 9
Revolving speed, that is, mechanism output revolving speed of the revolving speed of second gear ring 31, planet carrier 22 will gradually be risen by the minimum of top gear range
Up to the highest of the peak of the range and mechanism exports revolving speed.
The negative sense highest preset value of range and the highest preset value of bottom gear range, the revolving speed of duplex sun wheel shaft 1
Reach positive highest preset value；At this point, the speed ratio between duplex sun wheel shaft 1 and input shaft 9 has reached preset value, at mechanism
In the critical state that preparation switches from top gear to bottom gear.
In top gear state, adjust hydraulic variable displacement pump pivot angle make the revolving speed of duplex sun wheel shaft 1 by positive peak by
Step is reduced to zero, then by zero gradually negative sense increase；The second gear ring is passed to according to the characteristic of the second planet row and by input shaft 9
Revolving speed, that is, mechanism output revolving speed of 31 revolving speed, planet carrier 22 will be gradually reduced by the peak of top gear range；Meanwhile
According to the characteristic of the first planet row and the revolving speed of continually changing planet carrier 22, the revolving speed of the first gear ring 21 will be by positive maximum
Value gradually reduces；When the revolving speed of the first gear ring 21 is reduced to zero, mechanism output revolving speed reaches the minimum of top gear range and sets
The highest design value of evaluation and bottom gear range, mechanism are in the critical state for preparing to switch from top gear to bottom gear.
In aforementioned critical state, it is closed brake 6, opens clutch 5, completes the switching from top gear to bottom gear；This
When the first planet row it is in running order, the second planet row be detached from work；The piece revolving speed that rubs inside and outside it when due to closure brake 6 is equal
It is zero, therefore handoff procedure is without impact；Open clutch 5 due to being first closed after clutch 5 when switching, thus handoff procedure it is unpowered in
It is disconnected.
Under bottom gear state, the pivot angle for adjusting hydraulic variable displacement pump makes the revolving speed of duplex sun wheel shaft 1 by negative sense peak
Gradually reduce is zero；According to the characteristic of the first planet row and the revolving speed of the first gear ring 21, revolving speed, that is, mechanism of planet carrier 22
Output revolving speed will be gradually reduced by the peak of bottom gear range to zero.
It is mechanical that a kind of in-wheel driving is additionally provided in the present embodiment, including variable transmission mechanism described in the present embodiment.Tool
Body, which is tractor, offroad vehicle or loading machine etc..
Note that the above shows and describes the basic principles and main features of the present invention and the advantages of the present invention.The industry
Technical staff it should be appreciated that the present invention is not limited to the embodiments described above, described in above embodiment and specification
Merely illustrate the principles of the invention, without departing from the spirit and scope of the present invention, the present invention also have various change and
It improves, these changes and improvements all fall within the protetion scope of the claimed invention, and claimed range of the invention is by appended
Claims and its equivalent thereof.
Claims (10)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811563746.8A CN109442009A (en) | 2018-12-20 | 2018-12-20 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811563746.8A CN109442009A (en) | 2018-12-20 | 2018-12-20 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
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| Publication Number | Publication Date |
|---|---|
| CN109442009A true CN109442009A (en) | 2019-03-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811563746.8A Pending CN109442009A (en) | 2018-12-20 | 2018-12-20 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110985618A (en) * | 2019-12-26 | 2020-04-10 | 西安法士特汽车传动有限公司 | Double-planet row applied to transmission and transmission method thereof |
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| CN107131264A (en) * | 2017-06-21 | 2017-09-05 | 北京理工大学 | A kind of epicyclic transmission mechanism shifted gears based on belt flute profile brake and method |
| CN209444761U (en) * | 2018-12-20 | 2019-09-27 | 潍柴动力股份有限公司 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
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2018
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| JPH0642607A (en) * | 1992-07-21 | 1994-02-18 | Komatsu Ltd | Transmission steering device for tracked vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110985618A (en) * | 2019-12-26 | 2020-04-10 | 西安法士特汽车传动有限公司 | Double-planet row applied to transmission and transmission method thereof |
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Application publication date: 20190308 |
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