CN103671759A - Seven-gear speed changer - Google Patents

Seven-gear speed changer Download PDF

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Publication number
CN103671759A
CN103671759A CN201310731770.9A CN201310731770A CN103671759A CN 103671759 A CN103671759 A CN 103671759A CN 201310731770 A CN201310731770 A CN 201310731770A CN 103671759 A CN103671759 A CN 103671759A
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CN
China
Prior art keywords
gear
shaft
input
output
synchronizer
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.)
Pending
Application number
CN201310731770.9A
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Chinese (zh)
Inventor
静占国
朱春浩
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.)
Tianjin Santroll Electric Automobile Technology Co Ltd
Original Assignee
Tianjin Santroll Electric Automobile Technology Co Ltd
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 Tianjin Santroll Electric Automobile Technology Co Ltd filed Critical Tianjin Santroll Electric Automobile Technology Co Ltd
Priority to CN201310731770.9A priority Critical patent/CN103671759A/en
Publication of CN103671759A publication Critical patent/CN103671759A/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/12Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/003Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/20Transmissions using gears with orbital motion
    • F16H2200/203Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

Abstract

The invention relates to a seven-gear speed changer which is connected with a power input device through a double-clutch assembly. The seven-gear speed changer comprises two parallel input shafts, a middle shaft and an output shaft, a plurality of gears are respectively and movably or fixedly arranged on the seven-gear speed changer, and each rotating shaft transmits power through meshing of the gears. The seven-gear speed changer is provided with four synchronizer assemblies, the power input device is connected with at least one input shaft through the selective combination of the double-clutch assembly, and at least one of seven forward gears is established through the selective combination of at least one of four synchronizer assemblies. The nine pairs of gears and the four synchronizer assemblies are used, the seven forward torque gears are achieved, and compared with a traditional seven-gear speed changer, the improved seven-gear speed changer is smaller in size, simpler in structure and lower in manufacturing cost.

Description

Seven shift transmissions
Technical field
The present invention relates to a kind of seven shift transmissions, especially a kind of speed changer with seven forward gears, belongs to vehicle transmission gear, is specially adapted to the multi-gear transmission of vehicle.
Background technique
In order to improve drive system energy utilization efficiency, current way is to make power source work in its power consumption economic region as far as possible.For motor, its fuel-economy district is very narrow, under full operating mode, needs with gearbox, its outputting power to be carried out the variation of proper proportion, so that it is exported under operating mode at different power, motor itself can both work in its fuel-economy district.Because the no-load voltage ratio number (being gear number) of Fuel Economy and gearbox is closely related, thus explore many gear gearboxes so that power operation more high efficient and flexible be the trend of current gear box development.For parallel axes gearbox, due to its flexible design simple in structure and stability high, be the conventional gearbox-type in transmission system field always.The general gear logarithm of gearbox of parallel axes is suitable with gear number at present, such as 6 grades, approximately just needs 6-7 to gear, and namely 12-14 gear, and every gear is responsible for by different gears, and between different gears, gear can not share.Take two clutch gearboxes as example, realized, and even number gear 2,4,6 gears are realized by another part gear for odd number gear 1,3,5,7 gears by a part of gear, two clutch gearboxes can be realized more gear in this way.But even like this, double clutch gearbox need to approximately be twice in the gear of gear number equally, the larger bulk of the corresponding gearbox of more gear number, system instability increases, and the weight of system also increases thereupon.The present invention aims to provide a kind of novel gearbox, and profit adopts gear common principle, with the least possible gear, realizes gear number as much as possible.
Summary of the invention
The invention provides a kind of seven shift transmissions, there is twin-direction clutch assembly 2; The first input shaft 10 input shafts 11, selectively connect power input device 3 by twin-direction clutch assembly 2; Jack shaft 20, power is passed to described jack shaft 20 by described input shaft 10,11; Output shaft 30, power is passed to described output shaft 30 output by described jack shaft 20; Described input shaft 10,11, jack shaft 20, output shaft 30 are set parallel to each other; Have three groups of gear trains, every group of gear train has the input gear 101,102 being arranged on input shaft 10,11,103 respectively with the intermediate gear 201,202 being arranged on jack shaft 20,203 are meshed, with the output gear 301,302 being arranged on output shaft 30,303 are meshed respectively; Wherein the first input gear 101, the second input gear 102 and the 3rd input gear 103, wherein at least one gear is rotatably arranged on described the first input shaft 10; The first intermediate gear 201, the second intermediate gear 202, the 3rd intermediate gear 203, wherein at least two gears are rotatably arranged on described jack shaft 20; The first output gear 301, the second output gear 302 and the 3rd output gear 303 are rotatably arranged on described output shaft 30; Four synchronizer assemblies 40,50,60,70, described four synchronizer assemblies optionally make at least one at least one and described input shaft 10,11, jack shaft 20 and the output shaft 30 in the described gear of described three gear trains be coupled separately; And the selectivity of wherein said twin-direction clutch assembly 2 joint makes described power input device 3 and described input shaft 10, at least one interconnection in 11, and described four synchronizer assemblies 40,50, the selectivity of at least one in 60,70 engages at least one that set up seven forward gears.
As the first mode of execution of the present invention, described input shaft 10,11 configures coaxially to each other and can relatively rotate.
As the second mode of execution of the present invention, the first synchronizer assembly 40 in described four synchronizer assemblies 40,50,60,70 is optionally connected to described the first input shaft 10 by described the 3rd input gear 103.
On such scheme basis, described four synchronizer assemblies 40,50,60, the second synchronizer assembly 50 in 70 is optionally connected to described jack shaft 20 by described the first intermediate gear 201, and described the second intermediate gear 202 is optionally connected to described jack shaft 20.
On such scheme basis, the 3rd synchronizer assembly 60 in described four synchronizer assemblies 40,50,60,70 is optionally connected to described output shaft 30 by described the first output gear 301.
On such scheme basis, described four synchronizer assemblies 40,50,60, the 4th synchronizer assembly 70 in 70 is optionally connected to described output shaft 30 by described the second output gear 302, and described the 3rd output gear 303 is optionally connected to described output shaft 30.
On such scheme basis, from described twin-direction clutch assembly 2, described the first input gear 101, the second input gear 102, the 3rd input gear 103 are set on described input shaft 10,11 successively.
On such scheme basis, also comprise the 4th input gear 104, be fixedly installed on described the second input shaft 11, and be arranged between described the first input gear 101 and the second input gear 102; With the 4th output gear 304, be rotatably arranged on described output shaft 30, and be arranged between described the first output gear 301 and described the second output gear 302.
On such scheme basis, the 3rd synchronizer assembly 60 in described four synchronizer assemblies 40,50,60,70 is optionally connected to described output shaft 30 by described the 4th output gear 304.This scheme makes speed changer have the gear ratio of reversing gear.
The present invention also provides a kind of vehicle, has motor, speed changer, back axle and wheel, described speed changer uses the structure described in above-mentioned any one scheme, and described engine output shaft is by engaging and disengaging gear and described gearbox input shaft 10,11 connect, and described output shaft 30 connects described back axle and wheel.
This speed changer utilizes coordinating between gear and running shaft, synchronizer, uses 9 pinions to realize seven gear gear ratio, compared with traditional design, has saved 5 pinions, in conserve space and cost, makes speed changer structure simpler.
Accompanying drawing explanation
Fig. 1 is the present invention's seven shift transmission structural representations provided by the present invention.
Embodiment
Below in conjunction with accompanying drawing 1 contrast seven shift transmissions provided by the present invention, be elaborated.According to Fig. 1, seven shift transmissions totally represent by reference character 1, and it comprises the first input shaft 10, the second input shafts 11, jack shaft 20 and output shaft 30.Wherein, the first input shaft 10 is connected with twin-direction clutch 2 with the second input shaft 11, and is connected with motor (or other power source) output shaft (or flywheel) by twin-direction clutch 2.The first input shaft 10, the second input shafts 11, jack shaft 20 and output shaft 30 layout that is parallel to each other, and the first input shaft 10 and the second input shaft 11 arranged concentric, the second input shaft 11 is the concentric locking collar tubular axis that are coated on the first input shaft 10.Output shaft 30 connects final drive end, as wheel.
Double clutch 2 can be dry clutch assemblies or wet clutch assembly.In addition, double clutch assembly 2 has first clutch element and second clutch element.As known in the field of double clutch, first clutch element and second clutch element are realized respectively the connection of different power transmission path.Specifically, first clutch element connects the first input shaft 10, thereby realize motor output terminal, is connected with the first input shaft 10, forms the power transmission path along the first input shaft 10; Second clutch element connects the second input shaft 11, thereby realize motor output terminal, is connected with the second input shaft 11, forms the power transmission path along the second input shaft 11.
This speed changer also comprises three groups of pitch wheels: the first input gear 101, the first intermediate gear 201, the first output gear 301 are intermeshing; The second input gear 102, the second intermediate gear 202, the 3rd output gear 302 are intermeshing; The 3rd input gear 103, the 3rd intermediate gear 203, the 3rd output gear 303 are intermeshing.In addition, also comprise one group of reverse gear: the 4th input gear 104 and the 4th output gear 304.Wherein, the first input gear 10, the second input gear 102 and the 4th input gear 104 are connected in the second input shaft 11 in a fixed manner, jointly to rotate with the second input shaft 11; The 3rd input gear 103 is linked optionally with the first input shaft 10, to rotate or jointly not rotate with the first input shaft 10 is selectively common.The first intermediate gear 201 and the second intermediate gear 202 are linked optionally with jack shaft 20, to rotate or jointly not rotate with the first jack shaft 20 is selectively common; The 3rd intermediate gear 203 is connected in jack shaft 20 in a fixed manner, jointly to rotate with jack shaft 20.The first output gear 301, the second output gear 302, the 3rd output gear 303, the 4th output gear 304 are all connected in output shaft 30 in selectable mode, to rotate or jointly not rotate with output shaft 30 is selectively common.
More specifically, as accompanying drawing 1, from twin-direction clutch 2, the first input gear 101, the 4th input gear 104, the second input gear 102, the 3rd input gear 103 are set on the first input shaft 10 and the second input shaft 11 from left to right successively; On the first defeated axle 10 jack shaft 20 parallel with the second input shaft 11, set gradually from left to right: the first intermediate gear 201 being meshed with the first input gear 101, with the second intermediate gear 202 of the second input gear 102 engagement, with the 3rd intermediate gear 203 of the 3rd input gear 103 engagements; On the output shaft 30 parallel with jack shaft 20, set gradually from left to right: the first output gear 301 being meshed with the first intermediate gear 201, the 4th output gear 304 being meshed with the 4th input gear 104, with the second output gear 302 of the second intermediate gear 202 engagements, with the 3rd output gear 303 of the 3rd intermediate gear 203 engagements.
In addition, speed changer 1 of the present invention also comprises a plurality of synchronizer assemblies 40,50,60 and 70 that optionally activate.Synchronizer 40 is one side synchronizer, and it generally includes the shift fork (not shown) in engagement positio or in neutral or disengaging configuration by actuator (not shown) two-direction moving.In this embodiment, synchronizer 40 optionally activates, gear 103 is connected into rotation together with the first input shaft 10.Synchronizer 50,60 and 70 is Double-side Synchronous device, and each synchronizer in described synchronizer generally includes the shift fork (not shown) at least two engagement positios and in neutral or disengaging configuration by actuator (not shown) two-direction moving.In this embodiment, synchronizer 50 optionally activates, and gear 201 is connected into rotation together with jack shaft 20, and optionally activates, gear 202 is connected into rotation together with jack shaft 20.Synchronizer 60 optionally activates, and gear 301 is connected into rotation together with output shaft 30, and optionally activates, gear 304 is connected into rotation together with output shaft 30.Synchronizer 70 optionally activates, and gear 302 is connected into rotation together with output shaft 30, and optionally activates, gear 303 is connected into rotation together with output shaft 30.
Speed changer 1 can be passed to output shaft 30 by moment of torsion from the first input shaft 10 or the second input shaft 11 with at least seven forward gear torque ratios and at least one torque ratio of reversing gear.Selectivity by the one or more and double clutch 2 in synchronizer assembly engage to obtain forward gear torque ratio and reverse gear in torque ratio each.Those skilled in the art should be easily understood that, different speed ratios is associated with each torque ratio.In the situation that not departing from scope of the present invention, which synchronizer and which gear train are associated and can change with specific forward gear or the speed ratio that reverses gear.
It is to be noted, because some or several gears share in different forward gear torque ratios, make multispeed manual transmission in speed changer of the present invention and prior art obviously distinguish and come, utilize the gear of lesser amt to realize more speed ratio, make system mechanics structure simpler, volume is less, and power transfer path is shorter, and transmission efficiency is higher.In below describing, speed changer is respectively kept off the structure of speed ratio, the synchronizer action for not relating to, will not repeat.For example, while reversing gear speed ratio, in synchronizer 40,50,60,70, only have synchronizer 60 actions, gear 304 is connected into rotation together with output shaft 30, and synchronizer 40,50,70 is all placed in neutral, neither any one relevant gear is connected to relevant axle, now will only describe the action of synchronizer 60, do not describe the action of synchronizer 40,50,60,70.
For the torque ratio of reversing gear, clutch 2 is connected motor 3 output terminals with the second input shaft 11, and synchronizer 60 connects into rotation together with output shaft 30 by gear 304.More particularly, input torque from motor 3 is passed to the second input shaft 11 by double clutch 2, by gear 104, is passed to gear 304, by gear 304, is passed to synchronizer 122, from synchronizer 122, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the first gear torque ratio (gear advances), clutch 2 is connected motor 3 output terminals with the second input shaft 11, and synchronizer 60 connects into rotation together with output shaft 30 by gear 301.More particularly, input torque from motor 3 is passed to the second input shaft 11 by double clutch 2, by gear 101, be passed to gear 201, by gear 201, be passed to gear 301, by gear 301, be passed to synchronizer 60, by synchronizer 60, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the second gear torque ratio (second gear advances), clutch 2 is connected motor 3 output terminals with the second input shaft 11, and synchronizer 70 connects into rotation together with output shaft 30 by gear 302.More particularly, input torque from motor 3 is passed to the second input shaft 11 by double clutch 2, by gear 102, be passed to gear 202, by gear 202, be passed to gear 302, by gear 302, be passed to synchronizer 70, by synchronizer 70, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the 3rd gear torque ratio (ahead three gear), clutch 2 is connected motor 3 output terminals with the second input shaft 11, and synchronizer 50 connects into rotation together with jack shaft 20 by gear 201, synchronizer 70 connects into rotation together with output shaft 30 by gear 303.More particularly, input torque from motor 3 is passed to the second input shaft 11 by double clutch 2, by gear 101, be passed to gear 201, by gear 201, be passed to synchronizer 50, by synchronizer 50, be passed to jack shaft 20, by jack shaft 20, be passed to gear 203, by gear 203, be passed to gear 303, by gear 303, be passed to synchronizer 70, by synchronizer 70, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the 4th gear torque ratio (four gears advance), clutch 2 is connected motor 3 output terminals with the second input shaft 11, and synchronizer 50 connects into rotation together with jack shaft 20 by gear 202, synchronizer 70 connects into rotation together with output shaft 30 by gear 303.More particularly, input torque from motor 3 is passed to the second input shaft 11 by double clutch 2, by gear 102, be passed to gear 202, by gear 202, be passed to synchronizer 50, by synchronizer 50, be passed to jack shaft 20, by jack shaft 20, be passed to gear 203, by gear 203, be passed to gear 303, by gear 303, be passed to synchronizer 70, by synchronizer 70, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the 5th gear torque ratio (five gears advance), clutch 2 is connected motor 3 output terminals with the first input shaft 10, and synchronizer 40 connects into rotation together with the first input shaft 10 by gear 103, synchronizer 70 connects into rotation together with output shaft 30 by gear 303.More particularly, input torque from motor 3 is passed to the first input shaft 10 by double clutch 2, by the first input shaft 10, be passed to synchronizer 40, by synchronizer 40, be passed to gear 103, by gear 103, be passed to gear 203, by gear 203, be passed to gear 303, by gear 303, be passed to synchronizer 70, by synchronizer 70, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the 6th gear torque ratio (six gears advance), clutch 2 is connected motor 3 output terminals with the first input shaft 10, and synchronizer 40 connects into rotation together with the first input shaft 10 by gear 103, synchronizer 50 connects into rotation together with jack shaft 20 by gear 202, and synchronizer 70 connects into rotation together with output shaft 30 by gear 302.More particularly, input torque from motor 3 is passed to the first input shaft 10 by double clutch 2, by the first input shaft 10, be passed to synchronizer 40, by synchronizer 40, be passed to gear 103, by gear 103, be passed to gear 203, by gear 203, be passed to jack shaft 20, by jack shaft 20, be passed to synchronizer 50, by synchronizer 50, be passed to gear 202, by gear 202, be passed to gear 302, by gear 302, be passed to synchronizer 70, by synchronizer 70, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
For the 7th gear torque ratio (seven gears advance), clutch 2 is connected motor 3 output terminals with the first input shaft 10, and synchronizer 40 connects into rotation together with the first input shaft 10 by gear 103, synchronizer 50 connects into rotation together with jack shaft 20 by gear 201, and synchronizer 60 connects into rotation together with output shaft 30 by gear 301.More particularly, input torque from motor 3 is passed to the first input shaft 10 by double clutch 2, by the first input shaft 10, be passed to synchronizer 40, by synchronizer 40, be passed to gear 103, by gear 103, be passed to gear 203, by gear 203, be passed to jack shaft 20, by jack shaft 20, be passed to synchronizer 50, by synchronizer 50, be passed to gear 201, by gear 201, be passed to gear 301, by gear 301, be passed to synchronizer 60, by synchronizer 60, be passed to output shaft 30, from output shaft 30, be passed to clutch end.
The present invention passes through in conjunction with the different numbers of gears and the cooperation of synchronizer, having realized advances seven grades fall back one grade totally eight gear torque ratios, by sharing of gear, only use 11 pinions, in more existing modular design scheme, the sum of required gear is that 2 quantity that are multiplied by forward gear speed are added 3 gears about reversing gear, save a plurality of gears, embodied speed changer multiple beneficial effect.
In this specification, above gear combination is no longer described in detail; but the achieved gearbox mode of operation of the present invention is not limited to the scope of this specification and accompanying drawing indication; the motor that can realize by independent no-load voltage ratio speed changer involved in the present invention and motor independently gear combine; and utilize the designed speed changer of thought of the present invention, all belong to the protection domain that the present invention states.

Claims (10)

1. seven shift transmissions, have
Twin-direction clutch assembly (2);
The first input shaft (10) and the second input shaft (11), selectively connect power input device (3) by twin-direction clutch assembly (2);
Jack shaft (20), power is passed to described jack shaft (20) by described input shaft (10,11); Output shaft (30), power is passed to described output shaft (30) output by described jack shaft (20); Described input shaft (10,11), jack shaft (20), output shaft (30) are set parallel to each other; It is characterized in that,
There are three groups of gear trains, every group of gear train has the input gear (101 being arranged on input shaft (10,11), 102,103) respectively with the intermediate gear (201 being arranged on jack shaft (20), 202,203) be meshed, respectively with the output gear (301 being arranged on output shaft (30), 302,303) be meshed; Wherein the first input gear (101), the second input gear (102) and the 3rd input gear (103), wherein at least one gear is rotatably arranged on described the first input shaft (10);
The first intermediate gear (201), the second intermediate gear (202), the 3rd intermediate gear (203), wherein at least two gears are rotatably arranged on described jack shaft (20);
The first output gear (301), the second output gear (302) and the 3rd output gear (303) are rotatably arranged on described output shaft (30);
Four synchronizer assemblies (40,50,60,70), described four synchronizer assemblies optionally make at least one at least one and described input shaft (10,11), jack shaft (20) and the output shaft (30) in the described gear of described three gear trains be coupled separately;
And the selectivity of wherein said twin-direction clutch assembly (2) joint makes described power input device (3) and described input shaft (10,11) at least one interconnection in, and described four synchronizer assemblies (40,50,60,70) selectivity of at least one in engages at least one that set up seven forward gears.
2. seven shift transmissions according to claim 1, is characterized in that, described input shaft (10,11) configures coaxially to each other and can relatively rotate.
3. seven shift transmissions according to claim 1, it is characterized in that described four synchronizer assemblies (40,50,60,70) the first synchronizer assembly (40) in is optionally connected to described the first input shaft (10) by described the 3rd input gear (103).
4. seven shift transmissions according to claim 3, it is characterized in that, described four synchronizer assemblies (40,50,60,70) the second synchronizer assembly (50) in is optionally connected to described jack shaft (20) by described the first intermediate gear (201), and described the second intermediate gear (202) is optionally connected to described jack shaft (20).
5. seven shift transmissions according to claim 4, is characterized in that, the 3rd synchronizer assembly (60) in described four synchronizer assemblies (40,50,60,70) is optionally connected to described output shaft (30) by described the first output gear (301).
6. seven shift transmissions according to claim 5, it is characterized in that, described four synchronizer assemblies (40,50,60,70) the 4th synchronizer assembly (70) in is optionally connected to described output shaft (30) by described the second output gear (302), and described the 3rd output gear (303) is optionally connected to described output shaft (30).
7. seven shift transmissions according to claim 6, it is characterized in that, from described twin-direction clutch assembly (2), described the first input gear (101), the second input gear (102), the 3rd input gear (103) are set on described input shaft (10,11) successively.
8. seven shift transmissions according to claim 7, it is characterized in that, also comprise the 4th input gear (104), be fixedly installed on described the second input shaft (11) upper, and be arranged between described the first input gear (101) and the second input gear (102); With the 4th output gear (304), be rotatably arranged at described output shaft (30) upper, and be arranged between described the first output gear (301) and described the second output gear (302).
9. seven shift transmissions according to claim 8, is characterized in that, the 3rd synchronizer assembly (60) in described four synchronizer assemblies (40,50,60,70) is optionally connected to described output shaft (30) by described the 4th output gear (304).
10. a vehicle, there is motor, speed changer, back axle and wheel, it is characterized in that, described speed changer has the structure described in claim 1~9 any one, and described engine output shaft is by engaging and disengaging gear and described gearbox input shaft (10,11) connect, described output shaft (30) connects described back axle and wheel.
CN201310731770.9A 2013-12-26 2013-12-26 Seven-gear speed changer Pending CN103671759A (en)

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Application Number Priority Date Filing Date Title
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107747613A (en) * 2017-10-31 2018-03-02 宁波上中下自动变速器有限公司 Double-clutch automatic gearbox and the vehicle with the double-clutch automatic gearbox
CN110435409A (en) * 2018-05-03 2019-11-12 舍弗勒技术股份两合公司 Hybrid gearbox and hybrid vehicle
CN113348101A (en) * 2019-03-01 2021-09-03 舍弗勒技术股份两合公司 Hybrid power system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08334149A (en) * 1995-06-07 1996-12-17 Toyota Motor Corp Trans-axle
JP2003247610A (en) * 2002-02-22 2003-09-05 Nissan Motor Co Ltd Transmission for vehicle
CN101743142A (en) * 2007-05-14 2010-06-16 德国Fev发动机技术有限公司 The method of operation of hybrid power system and hybrid power system with two equipment gear devices
JP2010281415A (en) * 2009-06-05 2010-12-16 Toyota Motor Corp Multistage transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08334149A (en) * 1995-06-07 1996-12-17 Toyota Motor Corp Trans-axle
JP2003247610A (en) * 2002-02-22 2003-09-05 Nissan Motor Co Ltd Transmission for vehicle
CN101743142A (en) * 2007-05-14 2010-06-16 德国Fev发动机技术有限公司 The method of operation of hybrid power system and hybrid power system with two equipment gear devices
JP2010281415A (en) * 2009-06-05 2010-12-16 Toyota Motor Corp Multistage transmission

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107747613A (en) * 2017-10-31 2018-03-02 宁波上中下自动变速器有限公司 Double-clutch automatic gearbox and the vehicle with the double-clutch automatic gearbox
CN110435409A (en) * 2018-05-03 2019-11-12 舍弗勒技术股份两合公司 Hybrid gearbox and hybrid vehicle
CN110435409B (en) * 2018-05-03 2023-11-24 舍弗勒技术股份两合公司 Hybrid transmission and hybrid vehicle
CN113348101A (en) * 2019-03-01 2021-09-03 舍弗勒技术股份两合公司 Hybrid power system
CN113348101B (en) * 2019-03-01 2023-08-01 舍弗勒技术股份两合公司 Hybrid power system

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Application publication date: 20140326