CN2630567Y - Rotary power balance speed transmission - Google Patents
Rotary power balance speed transmission Download PDFInfo
- Publication number
- CN2630567Y CN2630567Y CN 03207174 CN03207174U CN2630567Y CN 2630567 Y CN2630567 Y CN 2630567Y CN 03207174 CN03207174 CN 03207174 CN 03207174 U CN03207174 U CN 03207174U CN 2630567 Y CN2630567 Y CN 2630567Y
- Authority
- CN
- China
- Prior art keywords
- gear
- input
- output
- train
- wheel mechanism
- 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.)
- Expired - Fee Related
Links
Images
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The utility model relates to a variable transmission device that is widely used in rotating equipment such as vehicle etc., which includes an input star wheel mechanism, an output star wheel mechanism, an absolute balance gear train and a non-absolute balance gear train; the input star wheel mechanism and the output star wheel mechanism are symmetrically installed on same axis, the gear train type of the two star wheel mechanisms is differential gear train, the absolute balance gear train and the non-absolute balance gear train are connected between the input and output differential gear trains respectively; the input shaft of the input star wheel mechanism and the output shaft of the output star wheel mechanism are arranged on the transmission case, the fixed axis of which are fixed on the transmission case. The utility model is the transmission of rotational speed and torsion of the input shaft and the output shaft with arbitrary variable transmission ratio, which are monitored, executed, coordinated and completed by the differential gear train, the absolute balance gear train and the non-absolute balance gear train of the input and output star wheel mechanisms, thus, the utility model drives the output shaft rotating with arbitrary variable transmission ratio, reaching power balanced speed change.
Description
Technical field
The utility model relates to a kind of speed changer of mechanical structure, is a kind of variable speed drive that can be widely used on the rotating machinerys such as vehicle specifically.
Background technique
Mechanical type gear in the transmission device is used very extensive, from use angle, generally divides two kinds of manual speed change and automatic speed changings, from function, the branch of stepped gearing and stepless change is arranged.These speed changers are with a long history, advantage such as reliable and stable, especially for the automatic transmission in the automobile, be connected with fluid torque converter thereafter, but depositing contradiction between automatic torque-changing and the transmission efficiency in order to overcome fluid torque converter itself, the planetary gears of connecting again in the fluid torque converter back is to satisfy the needs of automobile applying working condition.But automatic transmission will realize speed change, even infinite variable speed automatic structure, all less than the prerequisite that breaks away from artificial sampling, when shift speed change, can produce the motor overload operation if change velocity ratio too early, but delay to change the normal duty that velocity ratio can be wasted motor again; Certain infinite variable speed fully-automatic gearbox, its structure are too complicated, thereby the manufacture cost height, and price is expensive, is not easy to extensive use.
The model utility content
Goal of the invention of the present utility model is to provide a kind of input, output power balance, and input, output speed, torsion can be different, to adapt to the rotary power balanced type speed changer that the input and output velocity ratio produces the demand that changes arbitrarily.
The utility model rotary power balanced type speed changer comprises line of input star-wheel mechanism, output planetary wheel mechanism, absolute equilibrium train and non-absolute equilibrium train; Wherein line of input star-wheel mechanism and output planetary wheel mechanism symmetry are installed on the same axis, and both wheel set types are both differential gear train, are connected with non-absolute equilibrium train with the absolute equilibrium train respectively in the middle of input, the output differential gear train; Output shaft in input shaft in the line of input star-wheel mechanism and the output planetary wheel mechanism is installed on the case of transmission; Their dead axle all is fixed on the case of transmission.
The utility model rotary power balanced type speed changer, wherein the absolute equilibrium train is rigidly connected and is constituted for one by the input planet carrier and the output planetary frame in the output differential gear train of input in the differential gear train; Non-absolute equilibrium train is made of the velocity ratio speed change gear group of installing on non-absolute equilibrium axle and the non-absolute equilibrium axle; The velocity ratio change is stated gear train and is comprised input gear, output gear and several speed change gears between described input gear, output gear; Input gear, output gear respectively with the line of input star-wheel mechanism in gear ring and the engagement of the gear ring in the output planetary wheel mechanism.
The utility model rotary power balanced type speed changer, wherein the absolute equilibrium train is made of the excessive gear of installing on absolute equilibrium axle and the absolute equilibrium axle, excessively the gear two ends respectively with the line of input star-wheel mechanism in gear ring and the engagement of the gear ring in the output planetary wheel mechanism; Non-absolute equilibrium train is made of the velocity ratio speed change gear group of installing on non-absolute equilibrium axle and the non-absolute equilibrium axle; The velocity ratio change is stated gear train and is comprised input gear, output gear and several speed change gears between input gear, output gear; Input gear, output gear respectively with the line of input star-wheel mechanism in the input planet gear of input planet carrier and the output planetary wheel mechanism in the output planetary gear engagement of output planetary frame.
The utility model rotary power balanced type speed changer, wherein the planetary pinion in line of input star-wheel mechanism and the output planetary wheel mechanism is at least 3.
The utility model rotary power balanced type speed changer, wherein line of input star-wheel mechanism and output planetary wheel mechanism can exchange; Correspondingly importing gear and output gear exchanges.
The utility model rotary power balanced type speed changer, wherein absolute equilibrium train and non-absolute equilibrium train can be exchanged with input, output connecting of differential gear train.
The utility model rotary power balanced type speed changer, the wherein velocity ratio 1 of velocity ratio speed change gear group: (± X), wherein X is not equal to any positive number of 0, the sense of rotation of " ± " expression input gear or output gear.
The utility model rotary power balanced type speed changer, the wherein velocity ratio 1 of velocity ratio speed change gear group: (± X), wherein X is not equal to any positive number of 0, the sense of rotation of " ± " expression input gear or output gear.
The utility model rotary power balanced type speed changer, finish jointly by the differential gear train in the differential gear train in the line of input star-wheel mechanism, the output planetary wheel mechanism, absolute equilibrium train and non-absolute equilibrium train, the variation of the velocity ratio that transmission input shaft and output shaft bore (referring to rotating ratio and torsion ratio), so that adapt to the demand that requires any variation of the whole system velocity ratio that determined according to input shaft and output shaft, under the rotating speed of the input and output situation different, reach power-balance formula speed change with torsion.Thereby the realization stepless change reaches energy saving.
Description of drawings
Fig. 1 is the utility model structural representation;
Fig. 2 is the utility model transmission principle figure schematic representation;
Fig. 3 is another embodiment's of the utility model a transmission principle figure schematic representation.
Embodiment
As seen from Figure 1, the utility model rotary power balanced type speed changer is made up of input planet gear mechanism 1, output planetary wheel mechanism 2, absolute equilibrium train and non-absolute equilibrium train; Line of input star-wheel mechanism 1 and output planetary wheel mechanism 2 symmetries are installed on the same axis, and both wheel set types are both differential gear train, are connected with non-absolute equilibrium train with the absolute equilibrium train respectively in the middle of input, the output differential gear train; Input shaft 5 in the line of input star-wheel mechanism 1 and the output shaft 5 in the output planetary wheel mechanism 2 ', all rotation is installed on the case of transmission 6.Input, output planetary frame 4,4 ' rigid joint in input, the output differential gear train are one, constitute the absolute equilibrium axle 3 in the absolute equilibrium train, input gear 9 and output gear 10 in the velocity ratio speed change gear group 12 in the input in input, the output differential gear train, output gear 7,7 ' respectively and the non-absolute equilibrium train are connected with a joggle; Also comprise several speed change gears 11 in the velocity ratio speed change gear group in the non-absolute equilibrium train, be installed between input gear 9 and the output gear 10.Their dead axle all is fixed on the case of transmission 6.
Figure 2 shows that the transmission principle schematic representation of Fig. 1.Prior art is rotating speed and the torsion that the same input and output of transmission shaft transmission are arranged.Shown in Figure 2 in the utility model is exactly with the differential gear train in differential gear train in the line of input star-wheel mechanism 1 and the output planetary wheel mechanism 2, symmetry is installed on the same axis, and input, output differential gear train are connected with non-absolute equilibrium train with the absolute equilibrium train respectively.Input shaft 5 in the line of input star-wheel mechanism 1 and the output shaft 5 in the output planetary wheel mechanism 2 ' all rotation is installed on the case of transmission 6, input, output in the differential gear train planet carrier 4,4 ' being rigidly connected is one, constitute the absolute equilibrium train, in input, the output differential gear train input, output gear 7,7 ' respectively and non-absolute equilibrium train in velocity ratio speed change gear group 12 in input gear 9 and output gear 10 engagements; Ratio gear group 12 in the non-absolute equilibrium train; Also comprise several speed change gears 11, be installed in respectively between input gear 9 and the output gear 10.Their dead axle all is fixed on the case of transmission 6.
Fig. 3 is another embodiment's of the utility model a transmission principle schematic representation, this embodiment's structure is exactly with the differential gear train in differential gear train in the line of input star-wheel mechanism 1 and the output planetary wheel mechanism 2, symmetry is installed on the same axis, input, output differential gear train are connected with non-absolute equilibrium train with the absolute equilibrium train respectively, and input shaft 5 in the line of input star-wheel mechanism 1 and the output shaft 5 in the output planetary wheel mechanism 2 ' all rotation is installed on the case of transmission 6.Input in the differential gear train of input, output, output gear 7,7 ' respectively and absolute equilibrium axle 3 ' in transition gear 13 in two ends be connected with a joggle, the input in input, the output differential gear train, output planetary frame 4,4 ' on input, output gear 14,14 ' respectively and non-absolute equilibrium train in velocity ratio speed change gear group 12 in input gear 9 and output gear 10 be connected with a joggle; Comprise several speed change gears 11 in the velocity ratio speed change gear group 12 in the non-absolute equilibrium train, be installed between input gear 9 and the output gear 10.Their dead axle all is fixed on the case of transmission 6.
Fig. 2 is identical with model utility transmission principle shown in Figure 3, and just input in the transmission, output differential gear train exchange with absolute equilibrium train and being connected of non-absolute equilibrium train respectively.
The utility model is exactly to bear monitoring jointly, carry out, coordinate and finish the rotating speed of input shaft 5 and output shaft 5 ' in any variation of velocity ratio and the transmission of torsion by the differential gear train in the differential gear train in the line of input star-wheel mechanism 1, the output planetary wheel mechanism 2, absolute equilibrium train and non-absolute equilibrium train, the balance of power and power, thereby drive the rotation of output shaft 5 ' in the velocity ratio that changes arbitrarily, reach power-balance formula speed change.
Be example with Fig. 2 below, narrate transmission principle of the present utility model.In practice, for example: the state of automobile running, starting, go up a slope, smoothly, the road traveling of descending, input sun gear in the output planetary wheel mechanism 1 and the output sun gear in the output planetary wheel mechanism 2 are subjected to the restriction of motor car engine output power and automobile running resistance to produce speed discrepancy, torsion is poor, this speed discrepancy and torsion difference are exactly the velocity ratio of input sun gear and output sun gear, their velocity ratio relation is: input sun gear and output sun gear are power and power-balance, but rotating speed and rotating speed be inversely proportional to, and torsion and torsion are inversely proportional to, rotating speed and torsion are directly proportional, and torsion and rotating speed are directly proportional; And the driving force velocity ratio of input sun gear input is that rotating speed and torsion are inversely proportional to, the driving force velocity ratio relation of output sun gear output is that rotating speed and torsion are inversely proportional to, in order to solve the contradiction of this velocity ratio, just need the monitoring sampling, carry out and coordinate to finish the transmission of input sun gear and output sun gear rotating speed and torsion, the balance of power and power (argument is an energy conservation), monitoring sampling is planet wheel in the line of input star-wheel mechanism 1 and the planet wheel in the output planetary wheel mechanism 2, execution be gear ring 7 and 7 ', coordination is input gear 9 and the output gear 10 in the velocity ratio speed change gear group 12, execution and coordination are in order to adapt to any variation of velocity ratio, sometime or a certain period be up time rotation or static the rotation or the inverse time rotation, their rotational speed is by the decision of monitoring sampling velocity ratio parameter, they just produce and can adapt to any velocity ratio (but can not above the maximum transmission ratio of velocity ratio speed change gear group 12), absolute equilibrium axle 3 just needs to increase rotating speed or torsion separately when transmission rotating speed and torsion under the velocity ratio effect size is exactly a monitoring parameter, this monitoring parameter is the temporal difference of rotating speed and torque transmission (rotating speed and the torque transmission time difference: as import 100 newton and 1 and change, exporting 1 newton and 100 changes, they are finished at the same time, but the time in the input and output transmission is discrepant) a preceding part, this monitoring parameter is passed to execution by an end, pass to again and coordinate after the rotating speed and the torsion addition of remainder (rear section of former rotating speed and torque transmission time difference) on rotating speed that the other end returns and torsion and the absolute equilibrium axle, rotating speed after this addition and torsion are the same time for input sun gear and output sun gear, rotating speed after the addition and torsion just produce one and act on the input sun gear and the output sun gear is the combination epicyclic wheel of the rotating speed and the torsion of new transmission time driving force on the transmission time, it is power and power-balance for input sun gear and output sun gear, but rotating speed and rotating speed are inversely proportional to, torsion and torsion are inversely proportional to, rotating speed and torsion are directly proportional, torsion and rotating speed are directly proportional, this new proportionate relationship and former proportionate relationship are made opposite location and are changed, solved the difference of the former velocity ratio relation of input sun gear and output sun gear, just produce power-balance formula speed change, because any change of motoring condition, velocity ratio is to change arbitrarily, monitoring, carry out, the parameter respective change of coordinating, transmission time combination epicyclic wheel produces also respective change of respective drive ratio, just produce input sun gear and any velocity ratio that changes of the output sun gear in the output planetary wheel mechanism 2 in the line of input star-wheel mechanism 1, the combination epicyclic wheel of transmission driving force produces respective drive than (it is limited by the maximum transmission ratio of velocity ratio speed change gear group 12, be in gear range, can change arbitrarily), so entire mechanism has obtained rotary power balanced type speed change.Transmission principle shown in Figure 3 is identical with Fig. 2.
Claims (8)
1, a kind of rotary power balanced type speed changer comprises line of input star-wheel mechanism, output planetary wheel mechanism, absolute equilibrium train and non-absolute equilibrium train; It is characterized in that described line of input star-wheel mechanism (1) and output planetary wheel mechanism (2) symmetry are installed on the same axis, both wheel set types are both differential gear train, are connected with non-absolute equilibrium train with the absolute equilibrium train respectively in the middle of input, the output differential gear train; Output shaft (5 ') in input shaft in the line of input star-wheel mechanism (5) and the output planetary wheel mechanism is installed on the case of transmission (6); Their dead axle all is fixed on the case of transmission (6).
2, rotary power balanced type speed changer according to claim 1, it is characterized in that described absolute equilibrium train by input in the differential gear train input planet carrier (4) and the output planetary frame (4 ') in the output differential gear train to be rigidly connected be the one formation; Described non-absolute equilibrium train goes up the velocity ratio speed change gear group (12) of installing by non-absolute equilibrium axle (8) and non-absolute equilibrium axle (8) and constitutes; Described velocity ratio becomes to be stated gear train (12) and comprises that input gear (9), output gear (10) and several are positioned at the speed change gear (11) between described input gear (9), the output gear (10); Described input gear (9), output gear (10) respectively with line of input star-wheel mechanism (1) in gear ring (7) and the gear ring (7 ') in the output planetary wheel mechanism (2) engagement.
3, rotary power balanced type speed changer according to claim 1, it is characterized in that described absolute equilibrium train goes up the excessive gear of installing (13) by absolute equilibrium axle (3 ') and absolute equilibrium axle (3 ') and constitutes, excessively gear (13) two ends respectively with line of input star-wheel mechanism (1) in gear ring (7) and the gear ring (7 ') in the output planetary wheel mechanism (2) mesh; Described non-absolute equilibrium train goes up the velocity ratio speed change gear group (12) of installing by non-absolute equilibrium axle (8) and non-absolute equilibrium axle (8) and constitutes; Described velocity ratio becomes to be stated gear train (12) and comprises that input gear (9), output gear (10) and several are positioned at the speed change gear (11) between described input gear (9), the output gear (10); Described input gear (9), output gear (10) respectively with line of input star-wheel mechanism (1) in the input planet gear (14) of input planet carrier (4) and output planetary wheel mechanism (2) in output planetary gear (14 ') engagement of output planetary frame (4 ').
4, according to claim 1,2 described rotary power balanced type speed changers, it is characterized in that the planetary pinion in described input planet gear mechanism (1) and the output planetary gear mechanism (2) is at least 3.
5, rotary power balanced type speed changer according to claim 4 is characterized in that described input planet gear mechanism (1) and output planetary gear mechanism (2) can exchange; Correspondingly importing gear (9) and output gear (10) exchanges.
6,, it is characterized in that described absolute equilibrium train and non-absolute equilibrium train and input, output can exchange connecting of differential gear train according to claim 1 or 3 described rotary power balanced type speed changers.
7, rotary power balanced type speed changer according to claim 6, the velocity ratio 1 that it is characterized in that described velocity ratio speed change gear group (12): (± X), wherein X is not equal to any positive number of 0, the sense of rotation of " ± " expression input gear (9) or output gear (10).
8, rotary power balanced type speed changer according to claim 5, the velocity ratio 1 that it is characterized in that described velocity ratio speed change gear group (12): (± X), wherein X is not equal to any positive number of 0, the sense of rotation of " ± " expression input gear (9) or output gear (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 03207174 CN2630567Y (en) | 2003-08-06 | 2003-08-06 | Rotary power balance speed transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 03207174 CN2630567Y (en) | 2003-08-06 | 2003-08-06 | Rotary power balance speed transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2630567Y true CN2630567Y (en) | 2004-08-04 |
Family
ID=34288322
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 03207174 Expired - Fee Related CN2630567Y (en) | 2003-08-06 | 2003-08-06 | Rotary power balance speed transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2630567Y (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101571182A (en) * | 2008-04-30 | 2009-11-04 | 陈解生 | Step gearbox |
| CN110030334A (en) * | 2019-01-21 | 2019-07-19 | 王世峰 | The small-sized speed changer of variable diameter clutch |
| CN110454556A (en) * | 2019-07-01 | 2019-11-15 | 杨静 | Balancing device based on eddy-current brake |
| CN114179783A (en) * | 2021-12-21 | 2022-03-15 | 安徽江淮汽车集团股份有限公司 | Hybrid vehicle power control method and hybrid vehicle |
-
2003
- 2003-08-06 CN CN 03207174 patent/CN2630567Y/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101571182A (en) * | 2008-04-30 | 2009-11-04 | 陈解生 | Step gearbox |
| CN101571182B (en) * | 2008-04-30 | 2013-11-27 | 陈解生 | Step gearbox |
| CN110030334A (en) * | 2019-01-21 | 2019-07-19 | 王世峰 | The small-sized speed changer of variable diameter clutch |
| CN110454556A (en) * | 2019-07-01 | 2019-11-15 | 杨静 | Balancing device based on eddy-current brake |
| CN114179783A (en) * | 2021-12-21 | 2022-03-15 | 安徽江淮汽车集团股份有限公司 | Hybrid vehicle power control method and hybrid vehicle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101649895B (en) | Mixing type stepless speed change transmission device | |
| CN100436877C (en) | Split type continuously variable transmission | |
| CN101487519B (en) | Full-gear speed self-adapting continuously variable transmission | |
| CN2630567Y (en) | Rotary power balance speed transmission | |
| CN205013605U (en) | Derailleurs that keep off more and epicyclie gear thereof | |
| CN103511569B (en) | Double-planet train formula stepless auto gear | |
| CN202188076U (en) | Planetary gear continuously variable transmission | |
| CN104019195A (en) | Differential coupling automatic transmission | |
| CN109695685A (en) | A kind of collector-shoe gear of alterable features coefficient and its application | |
| CN204061762U (en) | A kind of differential coupling automatic transmission | |
| CN103511563B (en) | Double-planet train formula stepless auto gear | |
| CN101655142B (en) | Multiple speed transmission utilizing co-planar gear sets | |
| CN103527730B (en) | Double-planet train formula stepless auto gear | |
| CN203548743U (en) | Double-planet wheel system stepless automatic speed change mechanism | |
| CN103511567B (en) | Dual planetary gear system formula stepless auto gear | |
| CN205047757U (en) | Doubly shelves mechanism and variable speed assembly based on planetary mechanism | |
| CN2703163Y (en) | Planetary gear variable speed transmission | |
| Mavleev et al. | Design of a stepless torque converter for heavy trucks | |
| CN102261440B (en) | Continuously variable transmission | |
| CN201240263Y (en) | Dividing and convergent current type multi-shift automatic gear shift system based on planetary mechanism | |
| CN2871978Y (en) | Stepless speed adjuster | |
| CN2731178Y (en) | Planetary gear speed variator | |
| CN203548739U (en) | Double-planetary gear train type continuously variable transmission mechanism | |
| CN103511562A (en) | Double planetary gear train type stepless automatic speed change mechanism | |
| CN202326965U (en) | Automatic mechanical speed changing device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |