CN202901186U - Planet gear type manual transmission - Google Patents

Planet gear type manual transmission Download PDF

Info

Publication number
CN202901186U
CN202901186U CN 201220560385 CN201220560385U CN202901186U CN 202901186 U CN202901186 U CN 202901186U CN 201220560385 CN201220560385 CN 201220560385 CN 201220560385 U CN201220560385 U CN 201220560385U CN 202901186 U CN202901186 U CN 202901186U
Authority
CN
China
Prior art keywords
gear
planet
gears
sun gear
axle sleeve
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
Application number
CN 201220560385
Other languages
Chinese (zh)
Inventor
赵良红
范爱民
范梦吾
晁新华
张晓雷
丘利芳
吴峰
罗子聪
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shunde Vocational and Technical College
Shunde Polytechnic
Original Assignee
Shunde Vocational and Technical College
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Shunde Vocational and Technical College filed Critical Shunde Vocational and Technical College
Priority to CN 201220560385 priority Critical patent/CN202901186U/en
Application granted granted Critical
Publication of CN202901186U publication Critical patent/CN202901186U/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The utility model discloses a planet gear type manual transmission which comprises an input shaft, an output shaft, a middle shaft arranged between the input shaft and the output shaft, shaft sleeves and synchronizers or brakes and further comprises a double-row planet gear train and a planet row. The double-row planet gear train comprises small sun gears, big sun gears, short planet gears, long planet gears, a front planet support and front gear rings, wherein the front planet support is arranged on the short planet gears and the long planet gears, the small sun gears are meshed with the short planet gears, the long planet gears are respectively meshed with the big sun gears, the short planet gears and the front gear rings, and the small sun gears are fixedly connected with the big sun gears. Third planet gears of the planet row are arranged on a back planet support, third sun gears are meshed with the third planet gears, and the third planet gears are meshed with back gear rings. A Ravigneaux type and single-row planet gear speed change mechanism is adopted for the planet gear type manual transmission, an extreme small number of gears are used for achieving the purpose of five speed ratio gears, the axial and radial sizes of the transmission are reduced, and the layout design of an automobile structure is more flexible.

Description

The planetary gear type manual transmission
Technical field
The utility model relates to the automotive transmission technical field, more particularly, relates to a kind of planetary gear type manual transmission.
Background technique
In the normal running process of vehicle, motor is the link of making power, and clutch is the hinge of transferring power, and speed changer is the normal operation that realizes vehicle under different running condition, the i.e. link of distributed power.Automotive transmission is to set up for the required rotating speed of the rotating speed, torque and the vehicle traction that solve motor output and the contradiction between the torque.Speed changer is as the heart of transmission system, main task is transferring power, change the velocity ratio of automobile, enlarge the scope that drives wheel torque and rotating speed, make vehicle adapt to the driving cycle of various variations, motor is worked under desirable operating mode, under the constant prerequisite of engine torque direction, realize that falling back of automobile travel, realize neutral gear, interrupt the power that motor passes to wheel, make that motor can start, idling etc.The quality of road holding not only depends on motor, and also depends on to a great extent the coupling of speed changer and speed changer and motor.
Speed changer is divided into manual transmission and automatic transmission, wherein manual transmission is comparatively traditional transmission types, manual transmission must be according to the variation of automobile condition, by driver's conversion gear at any time, it operates and relatively bothers, but can more directly show driver's wish, thereby be liked to drive the personage and like.Manual transmission is that the gear train by different tooth ratios consists of, and the principle of its work is exactly by switching different gear trains, realizing the conversion of tooth ratio.Gear train is comprised of the gear of different-diameter, and the power transmission effect that different gear ratio reaches is fully not identical, and our said gear shift namely refers to the gear changing ratio.At present, manual gear of vehicle almost all adopts the speed changer of parallel-axis type, and forerunner's parallel-axis type speed variator need adopt three axles, the rear-guard parallel-axis type speed variator need adopt four axles, be three axle center, transmission shaft is all larger to the warp-wise size simultaneously, is unfavorable for the topology layout design of automobile.
The model utility content
The technical problems to be solved in the utility model is, a kind of manual transmission by brand new is provided, reduce speed changer axially and radial dimension, to overcome the deficiencies in the prior art.
For solving the problems of the technologies described above, the technical solution adopted in the utility model is: a kind of planetary gear type manual transmission, comprise input shaft, output shaft, be arranged on the jack shaft between described input shaft and the output shaft, axle sleeve, synchronizer or break, also comprise double planetary gear train, planet row, described double planetary gear train comprises small sun gear, large sun gear, short planet wheel, long planet wheel, front planet carrier, front ring gear, described short planet wheel, be provided with front planet carrier on the long planet wheel, described small sun gear and the engagement of short planet wheel, long planet wheel respectively with large sun gear, short planet wheel and front ring gear engagement, described small sun gear is fixedly connected with large sun gear; Described planet row comprises the 3rd sun gear, the third line star-wheel, rear planet carrier, rear gear ring, and described the third line star-wheel is arranged on the rear planet carrier, described the 3rd sun gear and the engagement of the third line star-wheel, described the third line star-wheel and the engagement of rear gear ring.
Preferably, described output shaft is fixedly connected with rear planet carrier, and the output shaft axle sleeve is set on the described output shaft, and described the 3rd sun gear is fixed on the described output shaft axle sleeve.
Preferably, axle sleeve and external axle sleeve in the middle of being socketed with on the described jack shaft, described jack shaft is fixedly connected with described front planet carrier, and described small sun gear is fixed on described jack shaft and puts, and described large sun gear is fixed on the described external axle sleeve.
Preferably, between described input shaft and jack shaft, be provided with high speed and reversing-gear synchronizer, the forward gears synchronizer connects described high speed and reversing-gear synchronizer and described middle axle sleeve, reversing-gear synchronizer connects forward gears synchronizer and external axle sleeve, between external axle sleeve and front planet carrier, front brake is set, gear ring and the 3rd sun gear also were provided with rear brake after Five-gear synchronizer connected on the 3rd sun gear.
Preferably, described front ring gear is fixedly connected with rear gear ring.
Preferably, the excircle of described front ring gear and rear gear ring is provided with the gear teeth, and described front ring gear and rear gear ring are connected with a joggle.
Preferably, described output shaft and input shaft homonymy arrange.
Compared with prior art, the utlity model has following advantage: the utility model is by adopting La Weinashi and single epicyclic transmission, and cooperate a plurality of synchronizers to use, make it both can reach the purpose that realizes five speed ratio gears with few number of gears, and can reduce the axial and radial dimension of speed changer, make the size of speed changer controlled, the vehicle structure layout design is more flexible, can reduce production costs simultaneously.
Description of drawings
Fig. 1 is the utility model planetary gear type manual transmission the first embodiment's power-transmitting unit schematic diagram.
Fig. 2 is 1 grade of operating condition figure of the utility model the first embodiment.
Fig. 3 is 2 grades of operating condition figure of the utility model the first embodiment.
Fig. 4 is 3 grades of operating condition figure of the utility model the first embodiment.
Fig. 5 is 4 grades of operating condition figure of the utility model the first embodiment.
Fig. 6 is 5 grades of operating condition figure of the utility model the first embodiment.
Fig. 7 is the utility model the first embodiment's reverse gear operating condition figure.
Fig. 8 is the utility model the second embodiment's power-transmitting unit schematic diagram.
Embodiment
Below, in conjunction with Figure of description and specific embodiment, the technical solution of the utility model is further described, should be appreciated that specific embodiment described herein only in order to explain the utility model, does not consist of restriction of the present utility model:
The first embodiment
Referring to Fig. 1 to Fig. 7, the utility model planetary gear type manual transmission comprises input shaft 11, a plurality of synchronizers or break, jack shaft 12, middle axle sleeve 13, external axle sleeve 14, output shaft axle sleeve 15, output shaft 16, double planetary gear train 51, planet row 52.
Double planetary gear train 51 adopts the La Weinashi gear shift, it comprises small sun gear 35, large sun gear 31, short planet wheel 34, long planet wheel 32, front planet carrier 36, front ring gear 33, small sun gear 35 meshes with large sun gear 31, short planet wheel 34 and front ring gear 33 respectively with short planet wheel 34 engagements, long planet wheel 32.
Planet row 52 adopts single planet row, and it comprises the 3rd sun gear 40, the third line star-wheel 39, rear planet carrier 37, rear gear ring 38, and output shaft is fixedly connected with rear planet carrier 37.The 3rd sun gear 40 and 39 engagements of the third line star-wheel, the third line star-wheel 39 and rear gear ring 38 engagements.
High speed and reversing-gear synchronizer 21 connect input shafts 11 and jack shafts 12.Forward gears synchronizer 22 connects at a high speed and reversing-gear synchronizer 21 and middle axle sleeve 13.Reversing-gear synchronizer 23 connects forward gears synchronizer 22 and external axle sleeve 14.Front brake 24 can be respectively fixedly external axle sleeve 14 or front planet carrier 36.Gear ring 38 and the 3rd sun gear 40 after Five-gear synchronizer 25 connects.Rear brake 26 can be fixed the 3rd sun gear 40.
The gear-change operation process is as follows:
As shown in Figure 1, during neutral state, high speed and reversing-gear synchronizer 21 are in the left side, are connected with input shaft 11, separate with jack shaft 12.Forward gears synchronizer 22 is in the right side, with at a high speed and reversing-gear synchronizer 21 and middle axle sleeve 13 all be connected.Reversing-gear synchronizer 23 is in the left side, is connected with forward gears synchronizer 22, separates with external axle sleeve 14.Front brake 24 mediates, and all separates with external axle sleeve 14 and front planet carrier 36.Five-gear synchronizer 25 is in the left side, is connected with rear gear ring 38, separates with the 3rd sun gear 40.Rear brake 26 is in the left side, is connected with the 3rd sun gear 40 it is fixed.
As shown in Figure 2, during one grade of running, front brake 24 moves to right, and front planet carrier 36 is fixed.This moment, power transmission line was: input shaft 11 High speed and reversing-gear synchronizer 21 Forward gears synchronizer 22 Middle axle sleeve 13 Small sun gear 35 Short planet wheel 34 Long planet wheel 32 Front ring gear 33 Rear gear ring 38 The third line star-wheel 39 Rear planet carrier 37 Output shaft 16.Position when all the other synchronizers are in neutral state.Among Fig. 2, heavy line represents power transmission line.
As shown in Figure 3, during the second gear running, front brake 24 moves to left, and external axle sleeve 14 is fixing, makes simultaneously large sun gear 31 also fixing.Position when all the other synchronizers are in neutral state.This moment, power transmission line was: its drive path and one grade are basic identical, also are by input shaft 11 High speed and reversing-gear synchronizer 21 Forward gears synchronizer 22 Middle axle sleeve 13 Small sun gear 35 Short planet wheel 34 Long planet wheel 32 Front ring gear 33 Rear gear ring 38 The third line star-wheel 39 Rear planet carrier 37 Output shaft 16, but large sun gear 31 is fixing during second gear, and front planet carrier revolves round the sun clockwise, has accelerated output speed.Position when all the other synchronizers are in neutral state.Among Fig. 3, heavy line represents power transmission line.
As shown in Figure 4, during the third gear running, high speed and reversing-gear synchronizer 21 move to right, and input shaft 11 is connected with jack shaft 12, make double planetary gear train 51 form an integral body.Jack shaft 12 rotates and orders about front planet carrier 36 and middle axle sleeve 13 synchronous rotaries, and this moment, power transmission line was: input shaft 11 High speed and reversing-gear synchronizer 21 at this moment, separate two branch roads, and wherein the power path of a branch road is: jack shaft 12 Front planet carrier 36 Short planet wheel 34 Long planet wheel 32.
The power path of another branch road is: forward gears synchronizer 22 Middle axle sleeve 13 Small sun gear 35 Long planet wheel 32.Then by long planet wheel 32 Front ring gear 33 Rear gear ring 38 The third line star-wheel 39 Rear planet carrier 37 Output shaft 16.
Position when all the other synchronizers are in neutral state.Among Fig. 4, heavy line represents power transmission line.
As shown in Figure 5, during the fourth gear running, high speed and reversing-gear synchronizer 21 move to right, and input shaft 11 is connected with jack shaft 12, and forward gears synchronizer 22 moves to left and separates with middle axle sleeve 13, and front brake 24 moves to left, and external axle sleeve 14 is fixing, make simultaneously large sun gear 31 also fixing.This moment, power transmission line was: input shaft 11 High speed and reversing-gear synchronizer 21 Jack shaft 12 Front planet carrier 36 Long planet wheel 32 Front ring gear 33 Rear gear ring 38 The third line star-wheel 39 Rear planet carrier 37 Output shaft 16.Position when all the other synchronizers are in neutral state.Among Fig. 5, heavy line represents power transmission line.
As shown in Figure 6, during five grades of runnings, high speed and reversing-gear synchronizer 21 move to right, and input shaft 11 is connected with jack shaft 12, and forward gears synchronizer 22 separates with middle axle sleeve 13, and front brake 24 moves to left, and external axle sleeve 14 is fixing, make simultaneously large sun gear 31 also fixing.Five-gear synchronizer 25 moves to right, and all is connected with the 3rd sun gear 40 with rear gear ring 38 it is connected, and rear brake 26 moves to right, and separates with the 3rd sun gear 40.This moment, power transmission line was: input shaft 11 High speed and reversing-gear synchronizer 21 Jack shaft 12 Front planet carrier 36 Long planet wheel 32 Front ring gear 33.At this moment, separate two branch roads, wherein the power path of a branch road is: rear gear ring 38 The third line star-wheel 39 Rear planet carrier 37.
The power path of another branch road is: Five-gear synchronizer 25 The 3rd sun gear 40 Rear planet carrier 37.Then be passed to output shaft 16 by rear planet carrier 37.
Position when all the other synchronizers are in neutral state.Among Fig. 6, heavy line represents power transmission line.
As shown in Figure 7, during the reverse gear running, forward gears synchronizer 22 moves to left and separates with middle axle sleeve 13, and reversing-gear synchronizer 23 moves to right and is connected with external axle sleeve 14, and front brake 24 is fixed front planet carrier 36.This moment, power transmission line was: input shaft 11 High speed and reversing-gear synchronizer 21 Forward gears synchronizer 22 Reversing-gear synchronizer 23 External axle sleeve 14 Large sun gear 31 Long planet wheel 32 Front ring gear 33 Rear gear ring 38 The third line star-wheel 39 Rear planet carrier 37 Output shaft 16.At this moment, input shaft 11 is opposite with the sense of rotation of output shaft 16.Position when all the other synchronizers are in neutral state.Among Fig. 7, heavy line represents power transmission line.
Each gear gear ratio calculation formula and velocity ratio size see table:
In the table:
Be front ring gear 33 numbers of teeth and the ratio of large sun gear 31 numbers of teeth, suppose =2
Be front ring gear 33 numbers of teeth and the ratio of small sun gear 35 numbers of teeth, suppose =2.3
Be rear gear ring 38 numbers of teeth and the ratio of the 3rd sun gear 40 numbers of teeth, suppose =2
The second embodiment
Referring to Fig. 8, the utility model planetary gear type manual transmission comprises the double planetary gear train 51 of La Weinashi and planet row 52.Double planetary gear train 51 and planet row 52 be layout on same axis not, input shaft connects double planetary gear train 51, planet row 52 connects output shaft, the excircle of front ring gear 33 is provided with the front ring gear gear teeth 60, the excircle of rear gear ring 38 is provided with the rear gear ring gear teeth 61, the front ring gear gear teeth 60 and the rear gear ring gear teeth 61 engagements, thereby the transmission of realization power.
The structure of double planetary gear train 51 is identical with the first embodiment, gear ring 38 and the 3rd sun gear 40 after Five-gear synchronizer 25 connects, it and rear brake 26 homonymies are arranged, when output shaft and input shaft homonymy, Five-gear synchronizer 25 and rear brake 26 are arranged in the left side (as shown in Figure 8) of the 3rd sun gear 40, when output shaft and input shaft not during homonymy, Five-gear synchronizer 25 and rear brake 26 are arranged in the right side of the 3rd sun gear 40.
The gear-change operation of each grade is identical with the first embodiment, no longer is being repeated in this description a bit.The change part, not creative work of doing based on the technical solution of the utility model or to the replacement that is equal to of technical solutions of the utility model local techniques feature all belongs to protection domain of the present utility model.

Claims (7)

1. planetary gear type manual transmission, comprise input shaft, output shaft, be arranged on the jack shaft between described input shaft and the output shaft, axle sleeve, synchronizer or break, it is characterized in that: also comprise double planetary gear train, planet row, described double planetary gear train comprises small sun gear, large sun gear, short planet wheel, long planet wheel, front planet carrier, front ring gear, described short planet wheel, be provided with front planet carrier on the long planet wheel, described small sun gear and the engagement of short planet wheel, long planet wheel respectively with large sun gear, short planet wheel and front ring gear engagement, described small sun gear is fixedly connected with large sun gear; Described planet row comprises the 3rd sun gear, the third line star-wheel, rear planet carrier, rear gear ring, and described the third line star-wheel is arranged on the rear planet carrier, described the 3rd sun gear and the engagement of the third line star-wheel, described the third line star-wheel and the engagement of rear gear ring.
2. planetary gear type manual transmission according to claim 1, it is characterized in that: described output shaft is fixedly connected with rear planet carrier, and the output shaft axle sleeve is set on the described output shaft, and described the 3rd sun gear is fixed on the described output shaft axle sleeve.
3. planetary gear type manual transmission according to claim 2, it is characterized in that: axle sleeve and external axle sleeve in the middle of being socketed with on the described jack shaft, described jack shaft is fixedly connected with described front planet carrier, described small sun gear is fixed on described jack shaft and puts, and described large sun gear is fixed on the described external axle sleeve.
4. planetary gear type manual transmission according to claim 3, it is characterized in that: between described input shaft and jack shaft, be provided with at a high speed and reversing-gear synchronizer, the forward gears synchronizer connects described high speed and reversing-gear synchronizer and described middle axle sleeve, reversing-gear synchronizer connects forward gears synchronizer and external axle sleeve, between external axle sleeve and front planet carrier, front brake is set, gear ring and the 3rd sun gear also were provided with rear brake after Five-gear synchronizer connected on the 3rd sun gear.
5. planetary gear type manual transmission according to claim 4, it is characterized in that: described front ring gear is fixedly connected with rear gear ring.
6. according to claim 1 to 4 arbitrary described planetary gear type manual transmissions, it is characterized in that: the excircle of described front ring gear and rear gear ring is provided with the gear teeth, and described front ring gear and rear gear ring are connected with a joggle.
7. planetary gear type manual transmission according to claim 6 is characterized in that: described output shaft and the setting of input shaft homonymy.
CN 201220560385 2012-10-30 2012-10-30 Planet gear type manual transmission Expired - Fee Related CN202901186U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 201220560385 CN202901186U (en) 2012-10-30 2012-10-30 Planet gear type manual transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 201220560385 CN202901186U (en) 2012-10-30 2012-10-30 Planet gear type manual transmission

Publications (1)

Publication Number Publication Date
CN202901186U true CN202901186U (en) 2013-04-24

Family

ID=48121858

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 201220560385 Expired - Fee Related CN202901186U (en) 2012-10-30 2012-10-30 Planet gear type manual transmission

Country Status (1)

Country Link
CN (1) CN202901186U (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102913598A (en) * 2012-10-30 2013-02-06 顺德职业技术学院 Planetary gear type manual transmission
CN103256352A (en) * 2013-04-28 2013-08-21 河南科技大学 Double-planet-row converging type multi-gear multi-clutch transmission
CN104179900A (en) * 2014-08-04 2014-12-03 洛阳舒诚机械设备有限公司 Special four-speed variation speed reducer for pile machine
CN110657201A (en) * 2018-06-29 2020-01-07 比亚迪股份有限公司 Transmission, power driving system and vehicle

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102913598A (en) * 2012-10-30 2013-02-06 顺德职业技术学院 Planetary gear type manual transmission
CN102913598B (en) * 2012-10-30 2016-03-23 顺德职业技术学院 Planetary gear type manual transmission
CN103256352A (en) * 2013-04-28 2013-08-21 河南科技大学 Double-planet-row converging type multi-gear multi-clutch transmission
CN104179900A (en) * 2014-08-04 2014-12-03 洛阳舒诚机械设备有限公司 Special four-speed variation speed reducer for pile machine
CN104179900B (en) * 2014-08-04 2016-08-31 洛阳舒诚机械设备有限公司 Special for pile machine four-speed variable moderator
CN110657201A (en) * 2018-06-29 2020-01-07 比亚迪股份有限公司 Transmission, power driving system and vehicle
CN110657201B (en) * 2018-06-29 2022-03-18 比亚迪股份有限公司 Transmission, power driving system and vehicle

Similar Documents

Publication Publication Date Title
CN102913598B (en) Planetary gear type manual transmission
CN201193688Y (en) Power-shift multi-speed transmission
CN101713448B (en) Double clutch type automatic gearbox
CN101463897B (en) Automatic transmission for vehicles
CN104728368B (en) One kind six keeps off planetary automatic transmission
CN103453087A (en) Multi-speed automatic transmission
CN102913597A (en) Seven-level planet automatic speed changer
CN202901186U (en) Planet gear type manual transmission
CN102797812B (en) Double-clutch speed changer
CN109737190B (en) Two double planetary gear four-gear automatic transmission of double separation and reunion
CN202100668U (en) Gear speed control mechanism of automotive six-speed automatic transmission
CN206159382U (en) 11 fast automatic gearbox drive mechanism
CN202812019U (en) Double-clutch speed changer
CN203331824U (en) Two-gear power transmission system of integrated planetary gear train of pure electric vehicle
CN101907150B (en) Double-clutch automatic transmission without reverse gear shaft
CN103256351B (en) Multi-clutch speed change gear
CN202690908U (en) Speed changer capable of pre-selecting gears
CN201359059Y (en) Multi-gear power shift planetary gearbox
CN209458357U (en) A kind of single planetary gear two-shift automatic speed variator of double clutches
CN107199875B (en) Hybrid vehicle transmission system
CN104006120A (en) Multi-gear automatic gearbox
CN203248625U (en) Multi-clutch transmission with convergent planetary row
CN203463568U (en) Double-clutch automatic transmission
CN103206505B (en) A kind of 5AT automatic transmission drive train suitable in small and medium-sized car is united
CN206072262U (en) It is a kind of to be based on double single-stage planetary mechanism variable transmission mechanism

Legal Events

Date Code Title Description
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20130424

Termination date: 20171030

CF01 Termination of patent right due to non-payment of annual fee