CN205047756U - Biax is shelves mechanism and variable speed assembly doubly - Google Patents
Biax is shelves mechanism and variable speed assembly doubly Download PDFInfo
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- CN205047756U CN205047756U CN201520402307.4U CN201520402307U CN205047756U CN 205047756 U CN205047756 U CN 205047756U CN 201520402307 U CN201520402307 U CN 201520402307U CN 205047756 U CN205047756 U CN 205047756U
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Abstract
The utility model discloses a biax is shelves mechanism and variable speed assembly doubly. This biax doubly shelves mechanism includes: the torque converter, the input shaft is connected the torque converter and is received input power through it, planetary motion mechanism, including power input piece, driving medium, driving control spare and power take off spare, a power input connection input shaft, power take off spare is connected to first output shaft, a clutching mechanism, selectivity braking driving control spare, second output shaft is with the coaxial setting of first output shaft, the 2nd clutching mechanism, selectivity joint input shaft and second output shaft. This biax is shelves mechanism and variable speed assembly doubly can realize the soft starting of unpowered interrupt gear shift and vehicle.
Description
Technical field
The utility model relates to a kind of power transmitting deice, particularly a kind of twin shaft based on planetary movement system times gear mechanism and speed changing assembly.
Background technique
Now, vehicle and speed changer correlation technique change development towards many grades just energetically.Gear is more, means and can obtain better power performance, lower energy consumption, higher transmission efficiency, lower exhaust emissions.Current high-grade car AT (AutomaticTransmission, hydraulic automatic speed variator) maximum gears reached nine forward gearss, it possesses better power performance, lower energy consumption, higher transmission efficiency, lower exhaust emissions than AT in the past, but meanwhile, it also more accurate, more complicated, cost is higher, more difficult maintenance etc.CVT (ContinuouslyVariableTransmission, stepless speed variator) countless many gears can be had in theory, but the intensity of CVT driving belt and the problem such as life problems and the sliding wear between driving belt and belt wheel limit the transmission efficiency of CVT in prior art, also limit the ability of CVT transmitting large torque, therefore, CVT is used on the car of huge discharge by there be limited evidence currently of.DCT (DualClutchTransmission, double-clutch speed changer) also can reach seven forward gearss at most at present.
In sum, automobile factory wishes commercial city that development & production goes out to have the speed changer of more gears, more economical, more environmental protection, but this all means the more component of needs, larger volume, larger weight, more complicated design, more accurate processing, higher cost of production and maintenance expenses.
Model utility content
The utility model provides a kind of twin shaft times gear mechanism and speed changing assembly, planetary body is provided with in this times of gear mechanism, and by realizing the Power output of friction speed ratio on two output shafts to the control of its different elements, to meet many gears and high-quality gear shift demand, realize times shelves of speed changer thus, torque-converters built-in in addition transmits soft to input power, can prevent transmission system from transshipping and realize the soft starting of vehicle.
The technical scheme in the invention for solving the above technical problem is to provide a kind of twin shaft times gear mechanism, comprising: torque-converters; Input shaft, is connected to receive input power with torque-converters; Planetary body, planetary body comprises power input, driving component, transmission control member and power output member, and wherein power input connects input shaft; First output shaft, for connecting power output member, the first clutch mechanism, for selectivity brake control piece, with make input shaft through driving component with First Speed than driving first output shaft; Second output shaft, is coaxially arranged with the first output shaft; Second clutch mechanism, engages input shaft and the second output shaft for selectivity, with make input shaft when without when driving component with second speed than driving second output shaft.
Wherein, twin shaft times gear mechanism comprises the 3rd clutch mechanism further, engages input shaft and the first output shaft for selectivity, with make input shaft when without when driving component with third speed than driving first output shaft.
Wherein, twin shaft times gear mechanism comprises the 4th clutch mechanism and the 5th clutch mechanism further, 3rd clutch mechanism selectivity engages input shaft and power output member, 4th clutch mechanism selectivity engaging power output member and the first output shaft, 5th clutch mechanism selectivity engaging power output member and the second output shaft, wherein the 4th clutch mechanism and the first clutch mechanism coordinate with First Speed than driving first output shaft, 4th clutch mechanism coordinates with third speed than driving first output shaft with the 3rd clutch mechanism, 5th clutch mechanism coordinates with the 4th speed than driving second output shaft with the first clutch mechanism.
Wherein, planetary body comprises sun gear, to be arranged at around sun gear and with the planetary gear set of sun gear outer gearing, with the gear ring of planetary gear set internal messing and the planet carrier that is arranged in planetary gear set, power input is gear ring, power output member is planet carrier, and transmission control member is sun gear.
Wherein, planetary body comprises sun gear, to be arranged at around sun gear and with the planetary gear set of sun gear outer gearing, with the gear ring of planetary gear set internal messing and the planet carrier that is arranged in planetary gear set, power input is gear ring, power output member is planet carrier, transmission control member is sun gear, and the first clutch mechanism comprises the braked part that coaxially arranges with sun gear and the brake component for braking braked part.
Another technological scheme that the utility model solves the problem adopted is to provide a kind of speed changing assembly, the speed changer that this speed changing assembly comprises the twin shaft times gear mechanism as described in above-mentioned any one and is connected with this twin shaft times gear mechanism.
Wherein, the selector that speed changer comprises multiple shifting gear and switches between multiple shifting gear, wherein the shifting gear of adjacent gear positions uses different selectors.
Twin shaft provided by the utility model times gear mechanism an output shaft can produce the Power output of two kinds of friction speed ratios wherein, when this times of gear mechanism and transmission combination, times shelves can be realized to the gear number of corresponding shaft in speed changer, thus realize more gear by the less number of gears, obtain better power performance, higher transmission efficiency, lower energy consumption, lower exhaust emissions, and can transmission assembly be done relatively less, more economical, simpler.Meanwhile, built-in torque-converters transmits soft to input power, can prevent transmission system from transshipping and realize the soft starting of vehicle.
Accompanying drawing explanation
Fig. 1 is the structural representation of the twin shaft times gear mechanism of the utility model first embodiment;
Fig. 2 is the structural representation of the twin shaft times gear mechanism of the utility model second embodiment;
Fig. 3 is the structural representation of the twin shaft times gear mechanism of the utility model the 3rd embodiment;
Fig. 4 is the schematic diagram of selector in the speed changer of the utility model one embodiment and the gear relations of distribution.
Embodiment
Fig. 1 is the structural representation of the twin shaft times gear mechanism of the utility model first embodiment.As shown in Figure 1, twin shaft times gear mechanism 1 comprises for receiving the input shaft 10 of power, the torque-converters 200 be connected with input shaft 10 and the first output shaft 121 and the second output shaft 122 from engine output shaft.First output shaft 121 and the second output shaft 122 coaxially arrange and are connected with speed changer 2.Input shaft 10 and between the first output shaft 121 and the second output shaft 122, a planetary body is set.Wherein, torque-converters 200 receives the input power that engine output shaft transmits, and is passed to planetary body by input shaft 10.This planetary body comprises sun gear 13, to be arranged at around sun gear 13 and with the planetary gear set 14 of sun gear 13 outer gearing, with the gear ring 15 of planetary gear set 14 internal messing and the planet carrier 16 that is arranged in planetary gear set 14.
Torque-converters 200 is hydraulic type torque-converters (FluidTorqueConverter), input shaft and the output shaft of hydraulic type torque-converters are contacted by automatic transmission fluid, when not being rigidly connected between working component, the shock and vibration produced in input power transmittance process can be eliminated, vehicle can softly be started to walk.In addition, fluid torque converter also has other features: overload protection performance and starting performance good; The rotating speed of output shaft can be greater than or less than the rotating speed of input shaft, and speed discrepancy is different along with the size of transmitting torque; Good automatic speed changing performance, when load increases, output speed declines automatically, otherwise automatically rises; Ensure that motor has stable working area, the transient changing of load can not be reflected on motor substantially; Change in design at many grades, fluid torque converter can locking lock-up clutch as soon as possible, allows the power of motor be directly delivered to fixed shaft type gear teeth wheels input shaft 13, to obtain better power character, acceleration and lower oil consumption.
The gear ring 15 of the planetary body of the present embodiment is connected with input shaft 10, using the power input as planetary body.Planet carrier 16 is connected with the first output shaft 121, using the power output member as planetary body.Planetary gear set 14 is as the driving component of planetary body, and sun gear 13 is as the transmission control member of planetary body.
In the present embodiment, twin shaft times gear mechanism 1 also comprises brake component 171 and is arranged at the braked part 172 on sun gear 13.Braked part 172 and sun gear 13 are coaxially fixed, and together form the first clutch mechanism of twin shaft times gear mechanism 1 with brake component 171.Gear ring 15 is provided with the first driving link 181, and correspondence is provided with the first driven member 182 on the second output shaft 122.First driven member 182 and the second output shaft 122 are coaxially fixed, and together form the second clutch mechanism of twin shaft times gear mechanism 1 with the first driving link 181.
The twin shaft times gear mechanism 1 of the present embodiment can produce following several drive state:
The first state, controls the first driving link 181 and the first driven member 182 is in separated state, and control brake component 171 and braked part 172 are in braking state simultaneously.Now, input shaft 10 drives the first output shaft 121 by gear ring 15, planetary gear set 14 and planet carrier 16 with First Speed ratio (deceleration).The input power that input shaft 10 receives slows down through gear ring 15, planetary gear set 14 and planet carrier 16 and is delivered to the first output shaft 121.
The second state, the first driving link 181 and the first driven member 182 that control the second clutch mechanism are in jointing state, and the brake component 171 and the braked part 172 that control the first clutch mechanism are in separated state simultaneously.Now, input shaft 10 drives the second output shaft 122 by the first driving link 181 of gear ring 15 and the second clutch mechanism and the first driven member 182 with second speed ratio (constant speed).The input power that input shaft 10 receives through the first driving link 181 of gear ring 15 and the second clutch mechanism and the first driven member 182 constant-speed transmission to the second output shaft 122.
The third state, first driving link 181 and the first driven member 182 are in half-clutch state, brake component 171 and braked part 172 are in half braking state simultaneously, input power is made to be passed to the first output shaft 121 and the second output shaft 122, to realize power failure-free gear shift through the first driving link 181 of planetary gear set 14 and the second clutch mechanism and the first driven member 182 respectively.
4th kind of state, controls the brake component 171 of the first clutch mechanism and the first driving link 181 of braked part 172 and the second clutch mechanism and the first driven member 182 and is all in separated state.Now, each parts of planetary gears export without determining, the input power of input shaft 10 cannot be delivered to the first output shaft 121 and the second output shaft 122.
In the present embodiment, second clutch mechanism is arranged between gear ring 15 and the second output shaft 122, and engage gear ring 15 and the second output shaft 122 for selectivity, but those skilled in the art can expect the second clutch mechanism being arranged at other positions to realize the joint between input shaft 10 and the second output shaft 122 completely, with make input shaft 10 when without planetary gear set 14 drive the second output shaft 122.Such as, driving link 181 is set directly on input shaft 10, or is arranged on other elements of associating with input shaft 10.
Fig. 2 is the structural representation of the twin shaft times gear mechanism of the utility model second embodiment.As shown in Figure 2, twin shaft times gear mechanism 3 comprises for receiving the input shaft 30 of power, the torque-converters 400 be connected with input shaft 30 and the first output shaft 321 and the second output shaft 322 from engine output shaft.First output shaft 321 and the second output shaft 322 coaxially arrange and are connected with speed changer 4.Input shaft 30 and between the first output shaft 321 and the second output shaft 322, a planetary body is set.Wherein, torque-converters 400 receives the input power that engine output shaft transmits, and is passed to planetary body by input shaft 30.This planetary body comprises sun gear 33, to be arranged at around sun gear 33 and with the planetary gear set 34 of sun gear 33 outer gearing, with the gear ring 35 of planetary gear set 34 internal messing and the planet carrier 36 that is arranged in planetary gear set 34.
The gear ring 35 of the planetary body of the present embodiment is connected with input shaft 30, using the power input as planetary body.Planet carrier 36 is connected with the first output shaft 321, using the power output member as planetary body.Planetary gear set 34 is as the driving component of planetary body, and sun gear 33 is as the transmission control member of planetary body.
Twin shaft times gear mechanism 3 also comprises brake component 371 and is arranged at the braked part 372 on sun gear 33.Braked part 372 and sun gear 33 are coaxially fixed, and together form the first clutch mechanism of twin shaft times gear mechanism 3 with brake component 371.Gear ring 35 is provided with the first driving link 381, and correspondence is provided with the first driven member 382 on the second output shaft 322.First driven member 382 and the second output shaft 322 are coaxially fixed, and together form the second clutch mechanism of twin shaft times gear mechanism 3 with the first driving link 381.Gear ring 35 is provided with the second driving link 391, and correspondence is provided with the second driven member 392 on planet carrier 36.Second driven member 392 is coaxially fixed with planet carrier 36, and together forms the 3rd clutch mechanism of twin shaft times gear mechanism 3 with the second driving link 391.
The twin shaft times gear mechanism 3 of the present embodiment can produce following several drive state:
The first state, the second driving link 391 and the second driven member 392 that control the first driving link 381 and the first driven member 382 and the 3rd clutch mechanism are in separated state, and the brake component 371 and the braked part 372 that control the first clutch mechanism are in braking state simultaneously.Now, input shaft 30 drives the first output shaft 321 by gear ring 35, planetary gear set 34 and planet carrier 36 with First Speed ratio (deceleration).The input power that input shaft 30 receives slows down through gear ring 35, planetary gear set 34 and planet carrier 36 and is delivered to the first output shaft 321.
The second state, the first driving link 381 and the first driven member 382 that control the second clutch mechanism are in jointing state, control the brake component 371 of the first clutch mechanism and the second driving link 391 of braked part 372 and the 3rd clutch mechanism and the second driven member 392 simultaneously and are in separated state.Now, input shaft 30 drives the second output shaft 322 by the first driving link 381 of gear ring 35 and the second clutch mechanism and the first driven member 382 with second speed ratio (constant speed).The input power that input shaft 30 receives through the first driving link 381 of gear ring 35 and the second clutch mechanism and the first driven member 382 constant-speed transmission to the second output shaft 322.
The third state, the second driving link 391 and the second driven member 392 that control the 3rd clutch mechanism are in jointing state, and the first driving link 381 and the first driven member 382 that control brake component 371 and braked part 372 and the second clutch mechanism are in separated state simultaneously.Now, input shaft 30 drives the first output shaft 321 by the second driving link 391 of gear ring 35, the 3rd clutch mechanism and the second driven member 392 and planet carrier 36 with third speed ratio (constant speed).Now, the second driving link 391 through gear ring 35, the 3rd clutch mechanism of receiving of input shaft 30 and the second driven member 392 and planet carrier 36 constant-speed transmission are to the first output shaft 321.
4th kind of state, the input power of control inputs axle 30 is through two clutch mechanismes or jointly transmit through one of them clutch mechanism and driving component.
5th kind of state, controls brake component 371 and braked part 372, first driving link 381 and the first driven member 382 and the second driving link 391 and the second driven member 392 and is all in separated state.Now, each parts of planetary gears export without determining, the input power of input shaft 30 cannot be delivered to the first output shaft 321 and the second output shaft 322.
Each component working state of speed changing assembly is formed below in conjunction with two table explanation twin shaft times gear mechanism 3 as follows speed changer 4 different from two kinds carries out combining:
| C1 | C2 | C3 | D1 | D2 | D3 | D4 | D5 | R | |
| 1 | √ | √ | |||||||
| 2 | √ | √ | |||||||
| 3 | √ | √ | |||||||
| 4 | √ | √ | |||||||
| 5 | √ | √ | |||||||
| 6 | √ | √ | |||||||
| 7 | √ | √ | |||||||
| 8 | √ | √ | |||||||
| R | √ | √ |
| C1 | C2 | C3 | D1 | D2 | D3 | D4 | D5 | R | |
| 1 | √ | √ | |||||||
| 2 | √ | √ | |||||||
| 3 | √ | √ | |||||||
| 4 | √ | √ | |||||||
| 5 | √ | √ | |||||||
| 6 | √ | √ | |||||||
| 7 | √ | √ | |||||||
| 8 | √ | √ | |||||||
| R1 | √ | √ | |||||||
| R2 | √ | √ |
Wherein, C1 represents the first clutch mechanism, and C2 represents the second clutch mechanism, and C3 represents the 3rd clutch mechanism, and D1 ~ D5 and R represents each engaging gear pair in speed changer 4 respectively.When C1, C2 or C3 are selected, represent that this clutch mechanism is in jointing state, when D1 ~ D5 and R is selected, represent through this gear mesh transferring power.
Above-mentioned twin shaft times gear mechanism 3 is utilized to combine with speed changer 4, can make that there is M+N+1 and (the first transmission input shaft be namely connected with the first output shaft 321 have M advance gear to gear, the second transmission input shaft be connected with the second output shaft 322 has N number of advance gear and 1 reverse gear) speed changer 4, be combined into the speed changing assembly with M × 2+N+1 gear (namely there is M × 2+N advance gear, 1 reverse gear).Or, make that there is M+N+1 and (namely the first transmission input shaft has M advance gear and 1 reverse gear to gear, second transmission input shaft has N number of advance gear) speed changer 4, be combined into and there is M × 2+N+2 gear (namely there is M × 2+N advance gear, 2 reverse gears) speed changing assembly, and can power failure-free gear shift be realized.The utility model adopts above-mentioned twin shaft times gear mechanism incorporating transmission, times shelves can be carried out to the gear number of one of them axle of speed changer, the less number of gears can be used to realize more gear, to obtain better power performance, higher transmission efficiency, lower energy consumption, lower exhaust emissions, and can transmission assembly be done relatively less.
3rd clutch mechanism of the present embodiment is arranged between gear ring 35 and planet carrier 36, and engage gear ring 35 and planet carrier 36 for selectivity, 3rd clutch mechanism can be arranged at other positions to realize the joint between input shaft 30 and the first output shaft 321 by other embodiments, with make input shaft 30 when without planetary gear set 34 drive the first output shaft 321.Such as, driving link 381 and driven member 382 are set directly at respectively on input shaft 30 and the first output shaft 321, or are arranged on other elements of associating with the first output shaft 321 with input shaft 30.
In addition, planetary movement system can also adopt other configuration modes and realize thus slowing down or driving up, and such as power input corresponds to sun gear, and power output member corresponds to planet carrier, and transmission control member corresponds to gear ring; Power input corresponds to planet carrier, and transmission control member corresponds to sun gear, and power output member corresponds to gear ring; Power input corresponds to planet carrier, and transmission control member corresponds to gear ring, and power output member corresponds to sun gear; Power input corresponds to gear ring, and transmission control member corresponds to planet carrier, and the corresponding sun gear of power output member or power input correspond to sun gear, and transmission control member corresponds to planet carrier, and power output member corresponds to gear ring.
Fig. 3 is the structural representation of the twin shaft times gear mechanism of the utility model the 3rd embodiment.As shown in Figure 3, twin shaft times gear mechanism comprises for receiving the input shaft 50 of power, the torque-converters 600 be connected with input shaft 50 and the first output shaft 521 and the second output shaft 522 from engine output shaft.First output shaft 521 and the second output shaft 522 coaxially arrange and are connected with speed changer.Input shaft 50 and between the first output shaft 521 and the second output shaft 522, a planetary body is set.Wherein, torque-converters 600 receives the input power that engine output shaft transmits, and is passed to planetary body by input shaft 50.This planetary body comprises sun gear 53, to be arranged at around sun gear 53 and with the planetary gear set 54 of sun gear 53 outer gearing, with the gear ring 55 of planetary gear set 54 internal messing and the planet carrier 56 that is arranged in planetary gear set 54.
The gear ring 55 of the planetary body of the present embodiment is connected with input shaft 50, using the power input as planetary body.Planet carrier 56 is connected with the second output shaft 522, using the power output member as planetary body.Planetary gear set 54 is as the driving component of planetary body, and sun gear 53 is as the transmission control member of planetary body.
In the present embodiment, twin shaft times gear mechanism adds the 4th clutch mechanism C4 and the 5th clutch mechanism C5 on the basis of clutch mechanism C1, C2, the C3 of three shown in Fig. 2.First clutch mechanism C1 is used for selectivity braking sun gear 53, second clutch mechanism C2 is used for selectivity and engages input shaft 50 and the second output shaft 522,3rd clutch mechanism C3 is used for the planet carrier 56 that selectivity engages input shaft 50 and is connected with the first output shaft 521,4th clutch mechanism C4 selectivity engages planet carrier 56 and the first output shaft the 521, five clutch mechanism C5 selectivity engages planet carrier 56 and the second output shaft 522.Thus, 4th clutch mechanism C4 and the first clutch mechanism C1 coordinates with First Speed than driving first output shaft 521,4th clutch mechanism C4 coordinates with the 3rd clutch mechanism C3 and coordinates with the 4th speed than driving second output shaft 522 with the first clutch mechanism C1 than driving first output shaft the 521, five clutch mechanism C5 with third speed.
Specifically, when the first clutch mechanism C1 and the 4th clutch mechanism C4 engages, other clutch mechanismes C2, C3, C5 be separated time, input shaft 50 through gear ring 55, planetary gear set 54, planet carrier 56 with First Speed than driving first output shaft 521; When the second clutch mechanism C2 engages, when other clutch mechanismes C1, C3, C4, C5 are separated, input shaft 50 directly with second speed than driving second output shaft 522; When the 3rd clutch mechanism C3 and the 4th clutch mechanism C4 engages, other clutch mechanismes C1, C2, C5 be separated time, input shaft 50 through planet carrier 56 with third speed than driving first output shaft 521; When the first clutch mechanism C1 and the 5th clutch mechanism C5 engages, other clutch mechanismes C2, C3, C4 be separated time, input shaft 50 through gear ring 55, planetary gear set 54, planet carrier 56 with the 4th speed than driving second output shaft 522.Wherein First Speed is than more identical than preferably with the 4th speed, and second speed, than more identical than preferably with third speed, can provide two kinds of velocity ratios respectively thus on the first output shaft 521 and the second output shaft 522.
In sum, twin shaft provided by the utility model times gear mechanism and speed changing assembly an output shaft can produce the Power output of two kinds of friction speed ratios wherein, when this times of gear mechanism and transmission combination, times shelves can be realized to the gear number of corresponding shaft in speed changer, thus realize more gear by the less number of gears, to obtain better power performance, higher transmission efficiency, lower energy consumption, lower exhaust emissions, can also power failure-free gear shift be realized, and transmission assembly can be done relatively less, more economical, simpler.
The speed changing assembly of the present embodiment may be used for the Power Drive Units such as vehicle, boats and ships, train.
Fig. 4 is the schematic diagram of selector in the speed changer of the utility model one embodiment and the gear relations of distribution.As shown in Figure 4, speed changer comprises multiple shifting gear D1, D2, D3, D4, D5 and R and multiple selector X1, X2, X3 (such as, the combination of above-described stepper motor and clutch collar) switched before above-mentioned shifting gear.Wherein, shifting gear D1, D2, D3, D4, D5 are respectively one grade of vehicle to five grades, and its gear ratio rises successively, and shifting gear R is reverse gear.In prior art designs, the shifting gear of adjacent gear positions (such as, one grade of corresponding shifting gear D1 and shifting gear D2 corresponding to second gear) use identical selector, therefore from a gear shift in the process of second gear, the corresponding selector first shifting gear D1 corresponding with a grade is separated, shifting gear D2 corresponding with second gear again engages, and extends shift time, also may cause power interruption.In the present embodiment, the shifting gear of adjacent gear positions uses different selectors.Specifically, one grade of corresponding shifting gear D1 and shifting gear D4 corresponding to fourth gear uses same selector X1, shifting gear D2 and five grade that second gear is corresponding corresponding shifting gear D5 uses same selector X2, and shifting gear D3 corresponding to third gear and shifting gear R corresponding to reverse gear uses same selector X3.Like this, when changing to second gear from one grade, while selector X1 is separated with shifting gear D1, selector X2 just can engage by shifting gear D2, has saved shift time, can not produce power interruption, improve property of automatic shft.
In the above-described embodiments, only exemplary description has been carried out to the utility model, but those skilled in the art can carry out various amendment when not departing from spirit and scope of the present utility model to the utility model after reading present patent application.
Claims (7)
1. a twin shaft times gear mechanism, is characterized in that, a described twin shaft times gear mechanism comprises:
Torque-converters, for receiving input power;
Input shaft, is connected to receive described input power with described torque-converters;
Planetary body, described planetary body comprises power input, driving component, transmission control member and power output member, and wherein said power input connects described input shaft;
First output shaft, for connecting described power output member;
First clutch mechanism, brakes described transmission control member for selectivity, drives described first output shaft to make described input shaft through described driving component with First Speed ratio;
Second output shaft, is coaxially arranged with described first output shaft; And
Second clutch mechanism, engages described input shaft and described second output shaft for selectivity, with make described input shaft when without when described driving component with second speed than drive described second output shaft.
2. twin shaft according to claim 1 times gear mechanism, it is characterized in that, described twin shaft times gear mechanism comprises the 3rd clutch mechanism further, engage described input shaft and described first output shaft for selectivity, with make described input shaft when without when described driving component with third speed than drive described first output shaft.
3. twin shaft according to claim 2 times gear mechanism, it is characterized in that, described twin shaft times gear mechanism comprises the 4th clutch mechanism and the 5th clutch mechanism further, described 3rd clutch mechanism selectivity engages described input shaft and described power output member, described 4th clutch mechanism selectivity engages described power output member and described first output shaft, described 5th clutch mechanism selectivity engages described power output member and described second output shaft, wherein said 4th clutch mechanism and described first clutch mechanism coordinate with described First Speed than driving described first output shaft, described 4th clutch mechanism coordinates with described third speed than driving described first output shaft with described 3rd clutch mechanism, described 5th clutch mechanism coordinates with the 4th speed than driving described second output shaft with described first clutch mechanism.
4. twin shaft times gear mechanism as claimed in claim 1, it is characterized in that, described planetary body comprises sun gear, to be arranged at around described sun gear and with the planetary gear set of described sun gear outer gearing, with the gear ring of described planetary gear set internal messing and the planet carrier that is arranged in described planetary gear set, described power input is described gear ring, described power output member is described planet carrier, and described transmission control member is described sun gear.
5. twin shaft times gear mechanism as claimed in claim 1, it is characterized in that, described planetary body comprises sun gear, to be arranged at around described sun gear and with the planetary gear set of described sun gear outer gearing, with the gear ring of described planetary gear set internal messing and the planet carrier that is arranged in described planetary gear set, described power input is described gear ring, described power output member is described planet carrier, described transmission control member is described sun gear, described first clutch mechanism comprises the braked part that coaxially arranges with described sun gear and the brake component for braking described braked part.
6. a speed changing assembly, is characterized in that, the speed changer that described speed changing assembly comprises the twin shaft times gear mechanism described in any one of claim 1-5 and is connected with described twin shaft times gear mechanism.
7. speed changing assembly as claimed in claim 6, it is characterized in that, the selector that described speed changer comprises multiple shifting gear and switches between described multiple shifting gear, wherein the described shifting gear of adjacent gear positions uses different described selectors.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520402307.4U CN205047756U (en) | 2015-06-11 | 2015-06-11 | Biax is shelves mechanism and variable speed assembly doubly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520402307.4U CN205047756U (en) | 2015-06-11 | 2015-06-11 | Biax is shelves mechanism and variable speed assembly doubly |
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| Publication Number | Publication Date |
|---|---|
| CN205047756U true CN205047756U (en) | 2016-02-24 |
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|---|---|---|---|
| CN201520402307.4U Expired - Fee Related CN205047756U (en) | 2015-06-11 | 2015-06-11 | Biax is shelves mechanism and variable speed assembly doubly |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113719607A (en) * | 2021-07-16 | 2021-11-30 | 重庆青山工业有限责任公司 | DCT power device adopting planetary gear transmission |
| CN113864408A (en) * | 2021-08-30 | 2021-12-31 | 重庆青山工业有限责任公司 | Device for controlling power transmission by adopting planetary gear and clutch |
-
2015
- 2015-06-11 CN CN201520402307.4U patent/CN205047756U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113719607A (en) * | 2021-07-16 | 2021-11-30 | 重庆青山工业有限责任公司 | DCT power device adopting planetary gear transmission |
| CN113864408A (en) * | 2021-08-30 | 2021-12-31 | 重庆青山工业有限责任公司 | Device for controlling power transmission by adopting planetary gear and clutch |
| CN113864408B (en) * | 2021-08-30 | 2024-04-05 | 重庆青山工业有限责任公司 | Device for controlling power transmission by adopting planetary gear and clutch |
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