CN106641128A - Double-gear clutch device and transmission assembly - Google Patents
Double-gear clutch device and transmission assembly Download PDFInfo
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- CN106641128A CN106641128A CN201710045886.5A CN201710045886A CN106641128A CN 106641128 A CN106641128 A CN 106641128A CN 201710045886 A CN201710045886 A CN 201710045886A CN 106641128 A CN106641128 A CN 106641128A
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- gear
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- input shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses a double-gear clutch device and a transmission assembly. The double-gear clutch device comprises a planet movement mechanism and two groups of speed ratio adjusting gears, wherein the planet movement mechanism and the two groups of speed ratio adjusting gears are connected between an input shaft and an output shaft, a mating gear of a first gear in the two groups of speed ratio adjusting gears is connected with a power output piece of the planet movement mechanism, and a mating gear of a second gear is arranged on the output shaft. According to the double-gear clutch device and the transmission assembly, a single planet row and the two groups of speed ratio adjusting gears can be utilized, so that the adjusting range of the output speed ratio can be greatly extended so as to satisfy the speed ratio requirement of transmission design, the fluctuation of engine speed of a vehicle can be reduced during gear shifting, and an engine is within the range of efficient operating performance.
Description
Technical field
The present invention relates to field is driven, more particularly to a kind of times gear arrangement of clutch and speed changing assembly.
Background technology
In order to obtain more preferable power performance, lower energy consumption, higher transmission efficiency, lower exhaust emissions, vehicle
, just energetically towards many gearization development, the current car gear of AT can reach ten advances for clutch and speed changer correlation technique
Gear.In Vehicle Shifting, speed is less than differential, and engine speed fluctuations are less, more can guarantee that engine in height
Effect runnability is interval.However, the speed of existing many gear designs is difficult to accomplish consistent than differential, such as when former 10AT's
In variable speed drives design, 1～10 tooth ratio that can realize of gear is followed successively by 4.70,2.99,2.15,1.80,1.52,1.28,1.00,
0.85th, 0.69,0.64, the speed of two neighboring gear than it is differential be followed successively by 1.57,1.39,1.19,1.18,1.19,1.28,
1.18、1.23、1.08.It can be seen that, the speed that existing design is difficult to meet two neighboring gear is even more less 1.2 than differential, this
When its some gear is changed, the fluctuation of speed of engine is very big, it is possible to which engine falls speed and causes greatly very much to turn round when there is upshift
Square output is less and sensation does not connect power, sensation of the power compared with "flesh" (nonproductive construction) when shifting gears.In addition, the structure of single planetary body sets
Meter, also it is extremely difficult realize 1.2 or the speed less than 1.2 than differential.Such as to realize that 1.2 speed than differential output, then needs gear ring defeated
Enter, planet carrier output, brake sun gear, and to meet sun gear with the rotating ratio of gear ring is 5, it means that if in P or N
During gear, engine speed is 2000RPM, then the rotating speed of sun gear is 10000RPM, and sun wheel speed is likely to too high causes knot
The serious consequences such as structure failure.
It can be seen that, how to realize that less and uniform speed needs a big technical barrier of solution than differential actually industry.
The content of the invention
In view of this, the present invention provides a kind of times gear arrangement of clutch and speed changing assembly, can greatly expand its output speed ratio
Adjustable range, to meet the speed of transmission design than demand, so that it is guaranteed that engine be in Effec-tive Function performance interval.
Times gear arrangement of clutch of one embodiment of the invention, as individual components engine output shaft and change-speed gearing are connected to
Between group input shaft, and including：Input shaft, is connected with engine output shaft, and receives power from engine output shaft；Output
Axle, output power is to change-speed gearing group input shaft；Planetary body, including power input, driving member, transmission control member with
And power output member, wherein power input is connected with input shaft；Speed-ratio regulation gear train first gear, its coupling gear with it is dynamic
Power output connects；Speed-ratio regulation gear train second gear, its coupling gear is located at output shaft；Arrestment mechanism, with transmission control
Part connects and for selective brake control piece so that input shaft Jing driving members and speed-ratio regulation gear train first gear,
Speed-ratio regulation gear train second gear is with First Speed than driving output shaft；Clutch, be connected to input shaft and output shaft it
Between, and for selectively engaging input shaft and output shaft so that input shaft is without driving member, the tooth of speed-ratio regulation gear train first
, with second speed than driving output shaft, the second speed ratio is 1 for wheel and speed-ratio regulation gear train second gear.
Alternatively, the planetary body include sun gear, be arranged at around sun gear and with sun gear external toothing
The gear ring of planetary gearsets and planetary gearsets internal messing and the planet carrier being arranged in planetary gearsets, sun gear is
Power input component, planet carrier is power output member, and gear ring is transmission control member, and planetary gearsets are driving member；The arrestment mechanism
Including brake component and braked part, braked part is coaxially connected with gear ring, and brake component is used to carry out selective system to braked part
It is dynamic；The clutch includes driving link and driven member, and driving link is coaxially connected with sun gear, and driven member coaxially connects with output shaft
Connect.
Alternatively, the planetary body include sun gear, be arranged at around sun gear and with sun gear external toothing
The gear ring of planetary gearsets and planetary gearsets internal messing and the planet carrier being arranged in planetary gearsets, gear ring is power
Input component, planet carrier is power output member, and sun gear is transmission control member, and planetary gearsets are driving member；The arrestment mechanism
Including brake component and braked part, braked part is coaxially connected with sun gear, and brake component is used to carry out selectivity to braked part
Braking；The clutch includes driving link and driven member, and driving link is coaxially connected with gear ring, and driven member coaxially connects with output shaft
Connect.
Alternatively, described times of gear arrangement of clutch further includes torsion damping mechanism, and the torsion damping mechanism is integrated in
On at least one of planetary body, arrestment mechanism and clutch, and torsion damping mechanism include be coaxially disposed and
The first rotatable parts that can be relatively rotated and the second rotatable parts and turning along the first rotatable parts and the second rotatable parts
The spring cushion of the dynamic rotatable parts of direction elastic connection first and the second rotatable parts.
Alternatively, an annular housing, the spring damping are formed between first rotatable parts and the second rotatable parts
Device is the curved spring being arranged in annular housing.
Alternatively, the curved spring is in series by the spring of at least two different coefficient of elasticity.
Alternatively, first rotatable parts and the second rotatable parts are symmetrically formed multiple Spring Cards along each circumferential respectively
Groove, spring cushion includes the multiple straight springs being placed in respectively in spring card slot.
Alternatively, it is mutually different including the coefficient of elasticity of at least two series connection or nesting in per group of corresponding spring card slot
Straight spring.
The speed changing assembly of one embodiment of the invention, including change-speed gearing group and be connected with the speed change group above-mentioned times gear
Arrangement of clutch.
Beneficial effect：Speed-ratio regulation gear train first gear provided in an embodiment of the present invention and speed-ratio regulation gear train second
Gear this two groups of speed-ratio regulation gears can further adjust input shaft on the basis of planetary body and drive output shaft
Speed ratio, so as to greatly expand the adjustable range of its fast ratio of output, to meet the speed of transmission design than demand, and then can allow car
Gearshift when reduce engine speed fluctuations, it is ensured that engine be in Effec-tive Function performance interval.
Description of the drawings
Fig. 1 is the structural representation of times gear arrangement of clutch of first embodiment of the invention；
Fig. 2 is the structural representation of times gear arrangement of clutch of second embodiment of the invention；
Fig. 3 is the structural representation of the embodiment of torsion damping mechanism one of the present invention.
Specific embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the skill to each exemplary embodiment provided by the present invention
Art scheme is clearly and completely described.In the case where not conflicting, the feature in following embodiment and embodiment can phase
Mutually combination.
Fig. 1 is referred to, is times gear arrangement of clutch of first embodiment of the invention.Described times of gear arrangement of clutch can be used as dynamic
One individual components of power apparatus are connected between engine output shaft and change-speed gearing group input shaft, for receiving from engine
Power, and it is negative to drive to export power by change-speed gearing group and the main reducing gear, the differential mechanism that are connected with change-speed gearing group etc.
Carry.Wherein, the power set that described times of gear arrangement of clutch is suitable for can be vehicle, ship, be certainly not limited to this；Accordingly
Ground, the load includes but is not limited to such as automotive wheel etc..
As shown in figure 1, times gear arrangement of clutch of the present embodiment includes input shaft 11, output shaft 12 and is connected to input
Planetary body 13, speed-ratio regulation gear train first gear 14, speed-ratio regulation gear train between axle 11 and output shaft 12
Two gears 15, arrestment mechanism 16, clutch 17.
Input shaft 11 is connected to receive power from engine output shaft with engine output shaft.
Output shaft 12 is connected to export power to change-speed gearing group input shaft with change-speed gearing group input shaft.
Planetary body 13 is connected between input shaft 11 and output shaft 12.Wherein, planetary body 13 is single file
Star motion, including sun gear 131, be arranged at around sun gear 131 and with the planetary gearsets of the external toothing of sun gear 131
132 and the gear ring 133 and the planet carrier 134 that is arranged in planetary gearsets 132 of the internal messing of planetary gearsets 132.Sun gear
131 are connected with input shaft 11, to receive power and as the power input of planetary body 13 by input shaft 11.Planet
Frame 134 is connected with output shaft 12, to export power and as the power output member of planetary body 13 by output shaft 12.Tooth
Circle 133 is the transmission control member of planetary body 13.Planetary gearsets 132 are the driving member of planetary body 13.
The coupling gear of speed-ratio regulation gear train first gear 14 is connected with planet carrier 134.
Speed-ratio regulation gear train second gear 15 is coaxially connected with speed-ratio regulation gear train first gear 14, and speed-ratio regulation
The coupling gear of gear train second gear 15 is located at output shaft 12.
Arrestment mechanism 16 includes brake component 161 and braked part 162.Braked part 162 is coaxially connected with gear ring 133, system
Moving part 161 is static component, and the static component can be case of transmission or other not revolving members, for braked part
162 carry out selective braking.Brake component 161 and braked part 162 are separated, and represent that arrestment mechanism 16 is separated.Brake component 161 and quilt
Brake component 162 is engaged, and represents that arrestment mechanism 16 is engaged, during engagement, the braking gear ring 133 of arrestment mechanism 16, and the power of input shaft 11
Planetary body 13 is transferred to, and then via speed-ratio regulation gear train first gear 14 and the tooth of speed-ratio regulation gear train second
Wheel 15 is transferred to output shaft 12.
Clutch 17 can be wet type or dry clutch, and it includes driving link 171 and driven member 172.Driving link 171
Coaxially connected with sun gear 131, driven member 172 is coaxially connected with output shaft 12.Driving link 171 and driven member 172 are separated, and are represented
Clutch 17 is separated.Driving link 171 and driven member 172 are engaged, and represent that clutch 17 is engaged, and input shaft 11 is dynamic during engagement
Power is directly output to output shaft 12 through clutch 17.
Above-mentioned arrestment mechanism 16 and clutch 17 can be considered a times controlling organization for gear arrangement of clutch, for various combination
Engaged, to control the bang path of power.Specifically：
Separate in arrestment mechanism 16, when clutch 17 is engaged, the power of input shaft 11 is not passed to planetary body
13, but be directly over clutch 17 and export to output shaft 12, now, input shaft 12 is with speed ratio 1 (i.e. constant speed ratio) driving
Output shaft 12.
Engage in arrestment mechanism 16, when clutch 17 is separated, the power of input shaft 11 successively Jing planetary bodies 13,
Speed-ratio regulation gear train first gear 14 and speed-ratio regulation gear train second gear 15 are transferred to output shaft 12.Road is transmitted in power
In footpath, speed-ratio regulation gear train first gear 14 and speed-ratio regulation gear train second gear 15 are adjusted jointly with planetary body 13
Section input shaft 11 drives the speed ratio of output shaft 12 to meet design requirement.For example, power is only by planetary body 13
When not transmitted by speed-ratio regulation gear train first gear 14 and speed-ratio regulation gear train second gear 15, input shaft 11 is with typical case
Value speed ratio drives output shafts 12 for 4, and through speed-ratio regulation gear train first gear 14 and speed-ratio regulation gear train second gear
After 15, the speed provided by speed-ratio regulation gear train first gear 14 and speed-ratio regulation gear train second gear 15 is compared for 0.3, i.e.,
Achievable input shaft 11 is with the speed of 4*0.3=1.2 than driving output shaft 12.
If speed is considered as into second speed ratio, planetary body 13 and speed-ratio regulation gear train first gear than 1
14 and the speed ratio that provides together of speed-ratio regulation gear train second gear 15 be First Speed ratio.That is, in this enforcement
In example, control arrestment mechanism 16 is engaged, you can so that the Jing driving members of input shaft 11 and two groups of speed-ratio regulation gears 14,15 are with first
Speed is than driving output shaft 12；Control clutch 17 is engaged, you can so that input shaft 11 is without driving member, first gear 14
With second gear 15 with second speed than driving output shaft 12.
It follows that in the present embodiment, speed-ratio regulation gear train first gear 14 and the tooth of speed-ratio regulation gear train second
15 this two groups of speed-ratio regulation gears of wheel can further adjust input shaft 11 on the basis of planetary body 13 and drive output
The speed ratio of axle 12, so as to greatly expand the adjustable range of its fast ratio of output, to meet the speed of transmission design than demand, for example in fact
Now less and uniform speed than differential, and then can allow vehicle shift when reduce engine speed fluctuations, it is ensured that engine is in
Effec-tive Function performance interval.
Fig. 2 is referred to, is times gear arrangement of clutch of second embodiment of the invention.Times gear arrangement of clutch of the present embodiment includes
Input shaft 21, output shaft 22 and the planetary body 23 being connected between input shaft 21 and output shaft 22, speed-ratio regulation tooth
Wheel group first gear 24, speed-ratio regulation gear train second gear 25, arrestment mechanism 26, clutch 27.
Input shaft 21 is connected to receive power from engine output shaft with engine output shaft.
Output shaft 22 is connected to export power to change-speed gearing group input shaft with change-speed gearing group input shaft.
Planetary body 23 is connected between input shaft 21 and output shaft 22.Wherein, planetary body 23 is single file
Star motion, including sun gear 231, be arranged at around sun gear 231 and with the planetary gearsets of the external toothing of sun gear 231
232 and the gear ring 233 and the planet carrier 234 that is arranged in planetary gearsets 232 of the internal messing of planetary gearsets 232.Gear ring
233 are connected with input shaft 21, to receive power and as the power input of planetary body 23 by input shaft 21.Planet
Frame 234 is connected with output shaft 22, to export power and as the power output member of planetary body 23 by output shaft 22.Too
Sun wheel 231 is the transmission control member of planetary body 23.Planetary gearsets 232 are the driving member of planetary body 23.
The coupling gear of speed-ratio regulation gear train first gear 24 is connected with planet carrier 234.
Speed-ratio regulation gear train second gear 25 is coaxially connected with speed-ratio regulation gear train first gear 24, and speed-ratio regulation
The coupling gear of gear train second gear 25 is located at output shaft 22.
Arrestment mechanism 26 includes brake component 261 and braked part 262.Braked part 262 is coaxially connected with sun gear 231,
Brake component 261 is static component, and the static component can be case of transmission or other not revolving members, for braked part
262 carry out selective braking.Brake component 261 and braked part 262 are separated, and represent that arrestment mechanism 26 is separated.Brake component 261 and quilt
Brake component 262 is engaged, and represents that arrestment mechanism 26 is engaged, during engagement, the braking sun gear 231 of arrestment mechanism 26, input shaft 21 it is dynamic
Power is transferred to planetary body 23, and then via speed-ratio regulation gear train first gear 24 and speed-ratio regulation gear train second
Gear 25 is transferred to output shaft 22.
Clutch 27 can be wet type or dry clutch, and it includes driving link 271 and driven member 272.Driving link 271
Coaxially connected with gear ring 233, driven member 272 is coaxially connected with output shaft 22.Driving link 271 and driven member 272 are separated, represent from
Close mechanism 27 to separate.Driving link 271 and driven member 272 are engaged, and represent that clutch 27 is engaged, the power of input shaft 21 during engagement
Output shaft 22 is directly output to through clutch 27.
Above-mentioned arrestment mechanism 26 and clutch 27 can be considered a times controlling organization for gear arrangement of clutch, for various combination
Engaged, to control the bang path of power.Specifically：
Separate in arrestment mechanism 26, when clutch 27 is engaged, the power of input shaft 21 is not passed to planetary body
23, but be directly over clutch 27 and export to output shaft 22, now, input shaft 22 is with speed ratio 1 (i.e. constant speed ratio) driving
Output shaft 22.
Engage in arrestment mechanism 26, when clutch 27 is separated, the power of input shaft 21 successively Jing planetary bodies 23,
Speed-ratio regulation gear train first gear 24 and speed-ratio regulation gear train second gear 25 are transferred to output shaft 22.Road is transmitted in power
In footpath, speed-ratio regulation gear train first gear 24 and speed-ratio regulation gear train second gear 25 are adjusted jointly with planetary body 23
Section input shaft 21 drives the speed ratio of output shaft 22 to meet design requirement.For example, power is only by planetary body 23
When not transmitted by speed-ratio regulation gear train first gear 24 and speed-ratio regulation gear train second gear 25, input shaft 21 is with typical case
Value speed ratio drives output shafts 22 for 1.4, and through speed-ratio regulation gear train first gear 24 and the tooth of speed-ratio regulation gear train second
After wheel 25, the speed provided by speed-ratio regulation gear train first gear 24 and speed-ratio regulation gear train second gear 25 is compared and is
0.857, you can realize input shaft 11 with the speed of 1.4*0.857=1.2 than driving output shaft 22.
If speed is considered as into second speed ratio, planetary body 23 and speed-ratio regulation gear train first gear than 1
24 and the speed ratio that provides together of speed-ratio regulation gear train second gear 25 be First Speed ratio.That is, in this enforcement
In example, control arrestment mechanism 26 is engaged, you can so that the Jing driving members of input shaft 21 and two groups of speed-ratio regulation gears 24,25 are with first
Speed is than driving output shaft 22；Control clutch 27 is engaged, you can so that input shaft 21 is without driving member, first gear 24
With second gear 25 with second speed than driving output shaft 22.
It follows that in the present embodiment, speed-ratio regulation gear train first gear 24 and the tooth of speed-ratio regulation gear train second
25 this two groups of speed-ratio regulation gears of wheel can further adjust input shaft 21 on the basis of planetary body 23 and drive output
The speed ratio of axle 22, so as to greatly expand the adjustable range of its fast ratio of output, to meet the speed of transmission design than demand, for example
Realize it is less and uniform fast than differential, and then can allow vehicle shift when reduce engine speed fluctuations, it is ensured that at engine
In Effec-tive Function performance interval.
It is the torsion damping mechanism being integrated on times gear arrangement of clutch of one embodiment of the invention refering to Fig. 3.The torsion
Damper mechanism 3 can be integrated in planetary body, the brake of times gear arrangement of clutch of above-mentioned Fig. 1 and embodiment illustrated in fig. 2
On at least one of structure and clutch, it includes the first rotatable parts 31, the second rotatable parts 32 and spring cushion
33.First rotatable parts 31 and the second rotatable parts 32 are coaxially disposed, and can relatively rotate.In the first rotatable parts 31 and second
It is formed with annular housing between rotatable parts 32, spring cushion 33 is the curved spring that is arranged in the annular housing, and edge
The rotation direction of the first rotatable parts 31 and the second rotatable parts 32 connects the first rotatable parts 31 and the second rotatable parts 32.It is excellent
Selection of land, the curved spring is in series by the spring of at least two different coefficient of elasticity, thus improves effectiveness in vibration suppression.
Certainly, other embodiment can be in the first rotatable parts 31 and the second rotatable parts 32 respectively along each circumferential symmetrical
Multiple spring card slots are formed, spring cushion 33 includes the multiple straight springs being placed in respectively in spring card slot.Also, it is preferred that
Ground, includes the mutually different straight spring of coefficient of elasticity of at least two series connection or nesting in per group of corresponding spring card slot.
Torsion damping mechanism 3 can be integrated on any one rotatable parts of above-mentioned times of gear arrangement of clutch, for example, first turn
The rotatable parts 32 of dynamic component 31 and second can be integrated in respectively the brake component of two arrestment mechanisms 16, at least one of 26 and
On braked part；Again for example, the first rotatable parts 31 are integrated on the gear ring 133 of the planetary body 13 shown in Fig. 1, and second
Rotatable parts 32 are integrated in the planetary gearsets 132 of planetary body 13.
Because the rotating speed from engine to vehicle transmission system and torque are periodically continually changing, this can make power train
The twisting vibration of generation；On the other hand because running car is on uneven road, automotive transmission is made angular speed occur unexpected
Change, can also cause twisting vibration.These twisting vibrations all can be to Parts for Power Train impacting property load so as to which the life-span contracts
It is short, or even part of damage.The embodiment of the present invention can be disappeared by the integrated torsional damper mechanism 3 on above-mentioned times of gear arrangement of clutch
Except twisting vibration and avoid resonance, prevent power train from transshipping, thus can by an individual components simultaneously integrated " clutch ", " subtract
Shake " etc. multiple function.
Further, because torsion damping mechanism 3 is using double rotatable parts structures and with certain mass, therefore by calculating
With configure the quality of the two, it is possible to achieve with double mass flywheel identical function, and then further integrated " double mass flywheel " work(
Energy.
The embodiment of the present invention also provides a kind of speed changing assembly, and it includes times gear arrangement of clutch (such as Fig. 1 of above-described embodiment
With any one shown in Fig. 2), therefore with identical beneficial effect.The applicable power set of the speed changing assembly are included but not
It is limited to vehicle, ship etc..
It should be understood that the foregoing is only embodiments of the invention, the scope of the claims of the present invention, every profit are not thereby limited
The equivalent structure made with description of the invention and accompanying drawing content or equivalent flow conversion, such as technical characteristic between each embodiment
Be combined with each other, or be directly or indirectly used in other related technical fields, the patent protection of the present invention is included in the same manner
In the range of.
Claims (9)
1. a kind of times gear arrangement of clutch, it is characterised in that it is defeated that described times of gear arrangement of clutch is connected to engine as individual components
Between shaft and change-speed gearing group input shaft, and including：
Input shaft, is connected with engine output shaft, and receives power from the engine output shaft；
Output shaft, output power is to change-speed gearing group input shaft；
Planetary body, including power input, driving member, transmission control member and power output member, wherein the power
Input component is connected with the input shaft；
Speed-ratio regulation gear train first gear, its coupling gear is connected with the power output member；
Speed-ratio regulation gear train second gear, it is coaxially connected with the speed-ratio regulation gear train first gear, and its coupling gear
Located at the output shaft；
Arrestment mechanism, is connected and for the selective braking transmission control member so that input shaft Jing is driven with transmission control member
Part and speed-ratio regulation gear train first gear, speed-ratio regulation gear train second gear are with First Speed than driving the output shaft；
Clutch, is connected between input shaft and output shaft, and for selectively engaging input shaft and output shaft so that it is described
Input shaft is without driving member, speed-ratio regulation gear train first gear and speed-ratio regulation gear train second gear with second speed ratio
The output shaft is driven, the second speed ratio is 1.
2. according to claim 1 times of gear arrangement of clutch, it is characterised in that the planetary body include sun gear,
It is arranged at around the sun gear and the planetary gearsets with the sun gear external toothing and the planetary gearsets internal messing
Gear ring and the planet carrier being arranged in the planetary gearsets, the sun gear is power input, and the planet carrier is
Power output, the gear ring is transmission control member, and the planetary gearsets are driving member；
The arrestment mechanism includes brake component and braked part, and the braked part is coaxially connected with gear ring, and the brake component is used
In carrying out selective braking to the braked part；
The clutch includes driving link and driven member, and the driving link is coaxially connected with the sun gear, the driven member
It is coaxially connected with the output shaft.
3. according to claim 1 times of gear arrangement of clutch, it is characterised in that the planetary body include sun gear,
It is arranged at around the sun gear and the planetary gearsets with the sun gear external toothing and the planetary gearsets internal messing
Gear ring and the planet carrier being arranged in the planetary gearsets, the gear ring is power input, and the planet carrier is power
Output, the sun gear is transmission control member, and the planetary gearsets are driving member；
The arrestment mechanism includes brake component and braked part, and the braked part is coaxially connected with sun gear, the brake component
For carrying out selective braking to the braked part；
The clutch includes driving link and driven member, and the driving link is coaxially connected with the gear ring, the driven member with
The output shaft is coaxially connected.
4. according to claim 1 times of gear arrangement of clutch, it is characterised in that described times of gear arrangement of clutch further includes to turn round
Turn damper mechanism, the torsion damping mechanism is integrated in the planetary body, the arrestment mechanism and the clutch
On at least one of structure, and the torsion damping mechanism include the first rotatable parts for being coaxially disposed and can relatively rotating and
Described in second rotatable parts and the rotation direction elastic connection along first rotatable parts and second rotatable parts
The spring cushion of one rotatable parts and second rotatable parts.
5. according to claim 4 times of gear arrangement of clutch, it is characterised in that first rotatable parts and described second turn
An annular housing is formed between dynamic component, the spring cushion is the curved spring being arranged in the annular housing.
6. according to claim 5 times of gear arrangement of clutch, it is characterised in that the curved spring is by least two different bullets
The spring of property coefficient is in series.
7. according to claim 4 times of gear arrangement of clutch, it is characterised in that first rotatable parts and described second turn
Dynamic component is symmetrically formed multiple spring card slots along each circumferential respectively, and the spring cushion includes being placed in the spring respectively
Multiple straight springs in draw-in groove.
8. according to claim 7 times of gear arrangement of clutch, it is characterised in that include in per group of corresponding spring card slot
At least two series connection or the mutually different straight spring of coefficient of elasticity of nesting.
9. a kind of speed changing assembly, it is characterised in that the speed changing assembly include speed changer and be connected with the speed changer as
Times gear arrangement of clutch described in any one of claim 1-8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710045886.5A CN106641128A (en) | 2017-01-20 | 2017-01-20 | Double-gear clutch device and transmission assembly |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710045886.5A CN106641128A (en) | 2017-01-20 | 2017-01-20 | Double-gear clutch device and transmission assembly |
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| CN106641128A true CN106641128A (en) | 2017-05-10 |
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| CN201710045886.5A Pending CN106641128A (en) | 2017-01-20 | 2017-01-20 | Double-gear clutch device and transmission assembly |
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| CN103591226A (en) * | 2013-11-11 | 2014-02-19 | 深圳市悦成汽车技术有限公司 | Double-shaft engaging and disengaging device and vehicle variable speed assembly |
| CN204253761U (en) * | 2014-09-26 | 2015-04-08 | 深圳市悦成汽车技术有限公司 | Times gear engaging and disengaging gear of motor vehicle driven by mixed power and vehicle speed variation assembly thereof |
| CN106122393A (en) * | 2016-07-29 | 2016-11-16 | 龚小娥 | There is arrangement of clutch and the speed changing assembly of gear function again |
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