CN203906678U - Double-shaft clutch device and vehicle speed change assembly - Google Patents
Double-shaft clutch device and vehicle speed change assembly Download PDFInfo
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- CN203906678U CN203906678U CN201320709247.1U CN201320709247U CN203906678U CN 203906678 U CN203906678 U CN 203906678U CN 201320709247 U CN201320709247 U CN 201320709247U CN 203906678 U CN203906678 U CN 203906678U
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Abstract
The utility model discloses a double-shaft clutch device and a vehicle speed change assembly. The double-shaft clutch device comprises an input shaft receiving input power, a planetary motion mechanism formed by a power input member, a transmission member, a transmission control member and a power output member, in which the power input member is connected with the input shaft, a first output shaft connected with the power output member, a first clutch mechanism selectively braking the transmission control member and enabling the input shaft to drive the first output shaft via the transmission member at a first speed ratio, a second output shaft coaxially arranged with the first output shaft, a second clutch mechanism selectively joining the input shaft and the second output shaft and enabling the input shaft to drive the second output shaft without the transmission member at a second speed ratio and further the double-shaft clutch device is integrated with a torsion damping mechanism. Powerless gear shift can be achieved via the double-shaft clutch device; and multifunction of clutch, shift-doubling and damping can be integrated via one independent component.
Description
[technical field]
The utility model relates to a kind of power transmitting deice, particularly a kind of double-shaft clutch device and vehicle speed variation assembly based on planetary movement system.
[background technique]
Now, vehicular clutch and speed changer correlation technique are just energetically towards many grades of changes, the development of high property of automatic shft.Gear is more, means and can obtain better power performance, lower energy consumption, higher transmission efficiency, lower exhaust emissions.Car has reached eight forward gearss with maximum gears of AT at present, it possesses better power performance, lower energy consumption, higher transmission efficiency, lower exhaust emissions than AT in the past, but meanwhile, it also more accurate, more complicated, cost is higher, more difficult maintenance etc.CVT can have countless many gears in theory, but the problems such as sliding wear in prior art between the intensity of CVT driving belt and life problems and driving belt and belt wheel have limited the transmission efficiency of CVT, also limited the ability of CVT transmitting large torque, therefore, there be limited evidence currently of is used in CVT on the car of large discharge capacity.DCT at most also can reach seven forward gearss at present.
In sum, automobile factory wishes commercial city that research and development produce more gears, more economical, more environmental protection and the higher speed changer of property of automatic shft, but this all means the more component of needs, larger volume, larger weight, more complicated design, more accurate processing, higher cost of production and maintenance expenses.Meanwhile, if torsional vibration that how relatively simple Structure Decreasing vehicle motor produces is also one of problem of studying for a long period of time of related domain.
[model utility content]
In order to solve many gears and the high-quality gear shift demand of vehicle in prior art, the utility model provides a kind of double-shaft clutch device, in this engaging and disengaging gear, be provided with planetary body and be integrated with torsion damping mechanism, and the power of realizing friction speed ratio by the different elements of planetary body is controlled on two output shafts is exported, to meet many gears and high-quality gear shift demand, realize the multiple function such as doubly shelves and vibration damping etc. of clutch, speed changer simultaneously.
The technical scheme in the invention for solving the above technical problem is to provide a kind of double-shaft clutch device, and this double-shaft clutch device comprises: input shaft, for receiving input power; Planetary body, planetary body comprises power input component, driving component, transmission control member and power output member, its medium power input component connects input shaft; The first output shaft, for connecting power output member, the first clutch mechanism, for selectivity braking transmission control member, so that input shaft drives the first output shaft through driving component with First Speed ratio; The second output shaft, coaxially arranges with the first output shaft; And second clutch mechanism, for selectivity, engage input shaft and the second output shaft so that input shaft without driving component in the situation that with second speed than driving the second output shaft.This double-shaft clutch device is further integrated with torsion damping mechanism, torsion damping mechanism comprise coaxial setting and in relative rotation the first rotatable parts with the second rotatable parts and along the first rotatable parts, be connected the spring cushion of the first rotatable parts and the second rotatable parts with the sense of rotation elasticity of the second rotatable parts.
Wherein, between the first rotatable parts and the second rotatable parts, form an annular housing, spring cushion is the curved spring being arranged in annular housing, or the first rotatable parts and the second rotatable parts are respectively along being circumferentially symmetrically formed a plurality of spring card slots separately, and spring cushion comprises a plurality of straight shape spring being placed in respectively in spring card slot.
Wherein, curved spring is in series by the spring of at least two different elasticity coefficient, or in every group of corresponding spring card slot, comprises at least two series connection or the nested mutually different straight shape spring of elasticity coefficient.
Wherein, double-shaft clutch device further comprises the 3rd clutch mechanism, for selectivity, engages input shaft and the first output shaft, so that input shaft drives the first output shaft with third speed ratio without driving component in the situation that.
Wherein, double-shaft clutch device further comprises the 4th clutch mechanism and the 5th clutch mechanism, the 3rd clutch mechanism selectivity engages input shaft and power output member, the 4th clutch mechanism selectivity engages power output member and the first output shaft, the 5th clutch mechanism selectivity engages power output member and the second output shaft, wherein the 4th clutch mechanism and the first clutch mechanism coordinate with First Speed than driving the first output shaft, the 4th clutch mechanism coordinates with the 3rd clutch mechanism with third speed than driving the first output shaft, the 5th clutch mechanism coordinates with the first clutch mechanism with the 4th speed than driving the second output shaft.
Wherein, planetary body comprises sun gear, be arranged at sun gear around and with the planetary gear set of sun gear outer gearing, with the gear ring meshing in planetary gear set and be arranged at the planet carrier in planetary gear set, power input component is gear ring, power output member is planet carrier, transmission control member is sun gear, torsion damping mechanism comprises the first torsion damping mechanism being integrated on gear ring, wherein the first rotatable parts of the first torsion damping mechanism are connected with input shaft with in the second rotatable parts one, the first rotatable parts of the first torsion damping mechanism and another in the second rotatable parts are provided with internal tooth, and with planetary gear set in mesh.
Wherein, planetary body comprises sun gear, be arranged at sun gear around and with the planetary gear set of sun gear outer gearing, with the gear ring meshing in planetary gear set and be arranged at the planet carrier in planetary gear set, power input component is gear ring, power output member is planet carrier, transmission control member is sun gear, the first clutch mechanism comprises braked part and the brake component for braked part is braked with the coaxial setting of sun gear, torsion damping mechanism comprises the second torsion damping mechanism being integrated on braked part, wherein the first rotatable parts of the second torsion damping mechanism are connected with sun gear with in the second rotatable parts one, brake component is braked another in the first rotatable parts of the second torsion damping mechanism and the second rotatable parts.
The utility model addresses the above problem another adopted technological scheme and is to provide a kind of vehicle speed variation assembly, and this vehicle speed variation assembly comprises the double-shaft clutch device as described in above-mentioned any one and the speed changer being connected with this double-shaft clutch device.
Wherein, speed changer comprises a plurality of shifting gears and the selector switching between a plurality of shifting gears, and wherein the shifting gear of adjacent gear is used different selectors.
Double-shaft clutch device provided by the utility model can be realized power failure-free gear shift.In addition, double-shaft clutch device provided by the utility model produces the power output of two kinds of friction speed ratios therein on an output shaft, when this engaging and disengaging gear and speed changer combination, can realize doubly shelves to the gear number of corresponding shaft in speed changer, can realize by the less number of gears more gear, to obtain better power performance, higher transmission efficiency, lower energy consumption, lower exhaust emissions, can realize power failure-free gear shift, and can transmission assembly be done relatively littlely, more economical, simpler, and then by an individual components while integrated " clutch ", the multiple functions such as " doubly shelves " and " vibration damping ".
[accompanying drawing explanation]
Fig. 1 is according to the structural representation of the utility model the first embodiment's double-shaft clutch device;
Fig. 2 is according to the structural representation of the utility model the second embodiment's double-shaft clutch device;
Fig. 3 is according to the structural representation of the utility model the 3rd embodiment's double-shaft clutch device;
Fig. 4 for according to the utility model the 4th embodiment for being integrated in the structural representation of the torsion damping mechanism on double-shaft clutch device;
Fig. 5 is according to the schematic diagram of the selector in the utility model the 5th embodiment's speed changer and the gear relations of distribution.
[embodiment]
As shown in Figure 1, Fig. 1 is according to the structural representation of the utility model the first embodiment's double-shaft clutch device.In the present embodiment, double-shaft clutch device 1 is connected between engine output shaft (not shown) and the input shaft of speed changer 2 as individual components, comprises for receive input shaft 10 and the first output shaft 121 and second output shaft 122 of input power from engine output shaft.The first output shaft 121 and the second output shaft 122 coaxially arrange, and are connected with speed changer 2.Between the input shaft 10 of double-shaft clutch device 1 and the first output shaft 121 and the second output shaft 122, a planetary body is set.This planetary body comprises sun gear 13, be arranged at sun gear 13 around and with the planetary gear set 14 of sun gear 13 outer gearings, with the gear ring 15 of planetary gear set 14 interior engagements and be arranged at the planet carrier 16 in planetary gear set 14.
In the present embodiment, gear ring 15 is connected with input shaft 10, the power input component of usining as planetary body.Planet carrier 16 is connected with the first output shaft 121, the power output member of usining as planetary body.Planetary gear set 14 is as the driving component of planetary body, and sun gear 13 is as the transmission control member of planetary body.
In the present embodiment, double-shaft clutch device 1 also comprises brake component 171 and is arranged at the braked part 172 on sun gear 13.Braked part 172 is coaxially fixing with sun gear 13, and together forms the first clutch mechanism of double-shaft clutch device 1 with brake component 171.
On gear ring 15, be provided with the first driving link 181, and correspondence is provided with the first driven member 182 on the second output shaft 122.The first driven member 182 and the second output shaft 122 are coaxially fixing, and together form the second clutch mechanism of double-shaft clutch device 1 with the first driving link 181.
In the present embodiment, the first and second clutch mechanismes can adopt known friction plate clutch or magnetic clutch.
Double-shaft clutch device 1 can produce following several drive state:
The first state, controls the first driving link 181 of the second clutch mechanism and the first driven member 182 in separated state, controls the brake component 171 of the first clutch mechanism and braked part 172 in braking state simultaneously.Now, input shaft 10 drives first output shaft 121 with First Speed than (deceleration) by gear ring 15, planetary gear set 14 and planet carrier 16.The input power that input shaft 10 receives slows down and is delivered to the first output shaft 121 through gear ring 15, planetary gear set 14 and planet carrier 16;
The second state, controls the first driving link 181 of the second clutch mechanism and the first driven member 182 in jointing state, controls the brake component 171 of the first clutch mechanism and braked part 172 in separated state simultaneously.Now, input shaft 10 drives second output shaft 122 with second speed than (constant speed) by the first driving link 181 and first driven member 182 of gear ring 15 and the second clutch mechanism.The input power process gear ring 15 that input shaft 10 receives and the first driving link 181 of the second clutch mechanism and the first driven member 182 constant-speed transmission are to the second output shaft 122;
The third state, control the first driving link 181 of the second clutch mechanism and the first driven member 182 in half-clutch state, the brake component 171 of control the first clutch mechanism and braked part 172 are in half braking state simultaneously, make input power through the first driving link 181 and first driven member 182 of planetary gear set 14 and the second clutch mechanism, be passed to the first output shaft 121 and the second output shaft 122 respectively, to realize power failure-free gear shift.
The 4th kind of state, controls the brake component 171 of the first clutch mechanism and the first driving link 181 of braked part 172 and the second clutch mechanism and the first driven member 182 in separated state.Now, each parts of planetary gears, without determining output, cannot be delivered to the input power of input shaft 10 the first output shaft 121 and the second output shaft 122, that is to say neutral gear.
In above-mentioned double-shaft clutch device, by using planetary body as the inside driving mechanism of engaging and disengaging gear and by controlling the different elements of planetary body, can realize power failure-free gear shift.
In the present embodiment, the second clutch mechanism is arranged between gear ring 15 and the second output shaft 122, and engage gear ring 15 and the second output shaft 122 for selectivity, but those of ordinary skills can expect that the second clutch mechanism is arranged to other positions realizes engaging between input shaft 10 and the second output shaft 122 completely, so that input shaft 10 drives the second output shaft 122 without planetary gear set 14 in the situation that.For example, driving link 181 is set directly on input shaft 10, or is arranged on other elements associated with input shaft 10.
As shown in Figure 2, Fig. 2 is according to the structural representation of the utility model the second embodiment's double-shaft clutch device.In the present embodiment, double-shaft clutch device 3 comprises for receive input shaft 30 and the first output shaft 321 and second output shaft 322 of power from engine output shaft (not shown).The first output shaft 321 and the second output shaft 322 coaxially arrange, and are connected with speed changer 4.Between the input shaft 30 of double-shaft clutch device 3 and the first output shaft 321 and the second output shaft 322, a planetary body is set.This planetary body comprises sun gear 33, be arranged at sun gear 33 around and with the planetary gear set 34 of sun gear 33 outer gearings, with the gear ring 35 of planetary gear set 34 interior engagements and be arranged at the planet carrier 36 in planetary gear set 34.
In the present embodiment, gear ring 35 is connected with input shaft 30, the power input component of usining as planetary body.Planet carrier 36 is connected with the first output shaft 321, the power output member of usining as planetary body.Planetary gear set 34 is as the driving component of planetary body, and sun gear 33 is as the transmission control member of planetary body.
In the present embodiment, double-shaft clutch device 3 also comprises brake component 371 and is arranged at the braked part 372 on sun gear 33.Braked part 372 is coaxially fixing with sun gear 33, and together forms the first clutch mechanism of double-shaft clutch device 3 with brake component 371.
On gear ring 35, be provided with the first driving link 381, and correspondence is provided with the first driven member 382 on the second output shaft 322.The first driven member 382 and the second output shaft 322 are coaxially fixing, and together form the second clutch mechanism of double-shaft clutch device 3 with the first driving link 381.
On gear ring 35, be provided with the second driving link 391, and correspondence is provided with the second driven member 392 on planet carrier 36.The second driven member 392 is coaxially fixing with planet carrier 36, and together forms the 3rd clutch mechanism of double-shaft clutch device 3 with the second driving link 391.
In the present embodiment, first, second, and third clutch mechanism can adopt known friction plate clutch or magnetic clutch.
Double-shaft clutch device 3 can produce following several drive state:
The first state, control the first driving link 381 of the second clutch mechanism and the second driving link 391 of the first driven member 382 and the 3rd clutch mechanism and the second driven member 392 in separated state, control the brake component 371 of the first clutch mechanism and braked part 372 in braking state simultaneously.Now, input shaft 30 drives first output shaft 321 with First Speed than (deceleration) by gear ring 35, planetary gear set 34 and planet carrier 36.The input power that input shaft 30 receives slows down and is delivered to the first output shaft 321 through gear ring 35, planetary gear set 34 and planet carrier 36;
The second state, control the first driving link 381 of the second clutch mechanism and the first driven member 382 in jointing state, control the brake component 371 of the first clutch mechanism and the second driving link 391 of braked part 372 and the 3rd clutch mechanism and the second driven member 392 in separated state simultaneously.Now, input shaft 30 drives second output shaft 322 with second speed than (constant speed) by the first driving link 381 and first driven member 382 of gear ring 35 and the second clutch mechanism.The input power process gear ring 35 that input shaft 30 receives and the first driving link 381 of the second clutch mechanism and the first driven member 382 constant-speed transmission are to the second output shaft 322;
The third state, control the second driving link 391 of the 3rd clutch mechanism and the second driven member 392 in jointing state, control the brake component 371 of the first clutch mechanism and the first driving link 381 of braked part 372 and the second clutch mechanism and the first driven member 382 in separated state simultaneously.Now, the second driving link 391 by gear ring 35, the 3rd clutch mechanism of input shaft 30 and the second driven member 392 and planet carrier 36 drive the first output shaft 321 with third speed than (constant speed).Now, the second driving link 391 through gear ring 35, the 3rd clutch mechanism that input shaft 30 receives and the second driven member 392 and planet carrier 36 constant-speed transmission are to the first output shaft 321;
The 4th kind of state, control any two clutch mechanismes in above-mentioned three clutch mechanismes in half-clutch or half braking state, control another one clutch mechanism in separated state simultaneously, the input power that makes input shaft 30 is through two clutch mechanismes or jointly transmit through one of them clutch mechanism and driving component, to realize power failure-free gear shift.
The 5th kind of state, the brake component 371 of control the first clutch mechanism and braked part 372, the first driving link 381 of the second clutch mechanism and the second driving link 391 of the first driven member 382 and the 3rd clutch mechanism and the second driven member 392 are all in separated state.Now, each parts of planetary gears, without determining output, cannot be delivered to the input power of input shaft 30 the first output shaft 321 and the second output shaft 322, that is to say neutral gear.
Below in conjunction with two table explanation double-shaft clutch devices 3 speed changers 4 different from two kinds below, combine and each component working state of forming doubly grade:
| ? | C1 | C2 | C3 | D1 | D2 | D3 | D4 | D5 | R |
| 1 | √ | ? | ? | √ | ? | ? | ? | ? | ? |
| 2 | ? | ? | √ | √ | ? | ? | ? | ? | ? |
| 3 | ? | √ | ? | ? | √ | ? | ? | ? | ? |
| 4 | √ | ? | ? | ? | ? | √ | ? | ? | ? |
| 5 | ? | ? | √ | ? | ? | √ | ? | ? | ? |
| 6 | ? | √ | ? | ? | ? | ? | √ | ? | ? |
| 7 | √ | ? | ? | ? | ? | ? | ? | √ | ? |
| 8 | ? | ? | √ | ? | ? | ? | ? | √ | ? |
| R | ? | √ | ? | ? | ? | ? | ? | ? | √ |
| ? | C1 | C2 | C3 | D1 | D2 | D3 | D4 | D5 | R |
| 1 | √ | ? | ? | √ | ? | ? | ? | ? | ? |
| 2 | ? | ? | √ | √ | ? | ? | ? | ? | ? |
| 3 | ? | √ | ? | ? | √ | ? | ? | ? | ? |
| 4 | √ | ? | ? | ? | ? | √ | ? | ? | ? |
| 5 | ? | ? | √ | ? | ? | √ | ? | ? | ? |
| 6 | ? | √ | ? | ? | ? | ? | √ | ? | ? |
| 7 | √ | ? | ? | ? | ? | ? | ? | √ | ? |
| 8 | ? | ? | √ | ? | ? | ? | ? | √ | ? |
| R1 | √ | ? | ? | ? | ? | ? | ? | ? | √ |
| R2 | ? | ? | √ | ? | ? | ? | ? | ? | √ |
Wherein C1 represents the first clutch mechanism, and C2 represents the second clutch mechanism, and C3 represents the 3rd clutch mechanism, and D1～D5 and R represent respectively each engaging gear pair in speed changer 4.When C1, C2 or C3 are when selected, represent that this clutch mechanism is in jointing state, when D1～D5 and R are when selected, represent through this gear mesh transferring power.
Utilize above-mentioned double-shaft clutch device 3 to combine with speed changer 4, can make to have M+N+1 gear (is had to M the gear that advances on the first transmission input shaft being connected with the first output shaft 321, on the second transmission input shaft being connected with the second output shaft 322, have N advance gear and 1 reverse gear) speed changer 4, be combined into and there is M * 2+N+1 gear the transmission assembly of (thering is M * 2+N the gear that advances, 1 reverse gear).Or, make to have M+N+1 gear (is had to M advance gear and 1 reverse gear on the first transmission input shaft, on the second transmission input shaft, have the N gear that advances) speed changer 4, be combined into and there is M * 2+N+2 gear and (there is M * 2+N the gear that advances, 2 reverse gears) transmission assembly, and can realize power failure-free gear shift.The utility model adopts above-mentioned twin shaft doubly to keep off engaging and disengaging gear incorporating transmission, can carry out doubly shelves to the gear number of one of them axle of speed changer, can use the less number of gears to realize more gear, to obtain better power performance, higher transmission efficiency, lower energy consumption, lower exhaust emissions, and can transmission assembly be done relatively littlely.
In the present embodiment, the 3rd clutch mechanism is arranged between gear ring 35 and planet carrier 36, and engage gear ring 35 and planet carrier 36 for selectivity, but those of ordinary skills can expect that the 3rd clutch mechanism is arranged to other positions realizes engaging between input shaft 30 and the first output shaft 321 completely, so that input shaft 30 drives the first output shaft 321 without planetary gear set 34 in the situation that.For example, driving link 381 and driven member 382 are set directly at respectively on input shaft 30 and the first output shaft 321, or are arranged on other elements associated with input shaft 30 and the first output shaft 321.
In addition, in other embodiments of the present utility model, planetary movement system can also adopt other configuration modes and realize and slow down or drive up thus, and for example power input component is corresponding to sun gear, power output member is corresponding to planet carrier, and transmission control member is corresponding to gear ring; Power input component is corresponding to planet carrier, and transmission control member is corresponding to sun gear, and power output member is corresponding to gear ring; Power input component is corresponding to planet carrier, and transmission control member is corresponding to gear ring, and power output member is corresponding to sun gear; Power input component is corresponding to gear ring, and transmission control member is corresponding to planet carrier, and the corresponding sun gear of power output member or power input component are corresponding to sun gear, and transmission control member is corresponding to planet carrier, and power output member is corresponding to gear ring.
As shown in Figure 3, Fig. 3 is according to the structural representation of the utility model the 3rd embodiment's double-shaft clutch device.In the present embodiment, double-shaft clutch device comprises for receive input shaft 50 and the first output shaft 521 and second output shaft 522 of power from engine output shaft (not shown).The first output shaft 521 and the second output shaft 522 coaxially arrange, and are connected with speed changer.Between the input shaft 50 of this double-shaft clutch device and the first output shaft 521 and the second output shaft 522, a planetary body is set.This planetary body comprises sun gear 53, be arranged at sun gear 53 around and with the planetary gear set 54 of sun gear 53 outer gearings, with the gear ring 55 of planetary gear set 54 interior engagements and be arranged at the planet carrier 56 in planetary gear set 54.
In the present embodiment, gear ring 55 is connected with input shaft 50, the power input component of usining as planetary body.Planet carrier 56 is as the power output member of planetary body.Planetary gear set 54 is as the driving component of planetary body, and sun gear 53 is as the transmission control member of planetary body.
In the present embodiment, double-shaft clutch device has further increased the 4th clutch mechanism C4 and the 5th clutch mechanism C5 on the basis of the first clutch mechanism C1 shown in Fig. 2, the second clutch mechanism C2 and the 3rd clutch mechanism C3.Wherein, the first clutch mechanism C1 is for selectivity braking sun gear 53, the second clutch mechanism C2 engages input shaft 50 and the second output shaft 522 for selectivity, and the 3rd clutch mechanism C3 engages input shaft 50 and the planet carrier 56 being connected with the first output shaft 521 for selectivity, the concrete structure of above-mentioned clutch mechanism is identical with the embodiment shown in Fig. 2 with working principle, does not repeat them here.
Further, the 4th clutch mechanism C4 selectivity engages planet carrier 56 and the first output shaft 521, the five clutch mechanism C5 selectivity joint planet carrier 56 and the second output shafts 522.Thus, the 4th clutch mechanism C4 and the first clutch mechanism C1 coordinate with First Speed than driving the first output shaft 521, the 4th clutch mechanism C4 coordinates with the 3rd clutch mechanism C3 with third speed than driving the first output shaft 521, the five clutch mechanism C5 to coordinate with the first clutch mechanism C1 with the 4th speed than driving the second output shaft 522.
Specifically, as the first clutch mechanism C1 and the 4th clutch mechanism C4 joint, other clutch mechanismes C2, C3, when C5 is separated, input shaft 50 is through gear ring 55, planetary gear set 54, planet carrier 56 drives the first output shaft 521 with First Speed ratio, when the second clutch mechanism C2 engages, and other clutch mechanismes C1, C3, C4, when C5 is separated, input shaft 50 directly drives the second output shaft 522 with second speed ratio, as the 3rd clutch mechanism C3 and the 4th clutch mechanism C4 joint, other clutch mechanismes C1, C2, when C5 is separated, input shaft 50 drives the first output shaft 521 through planet carrier 56 with third speed ratio, as the first clutch mechanism C1 and the 5th clutch mechanism C5 joint, other clutch mechanismes C2, C3, when C4 is separated, input shaft 50 is through gear ring 55, planetary gear set 54, planet carrier 56 drives the second output shaft 522 with the 4th speed ratio, wherein First Speed is than more identical than preferentially with the 4th speed, second speed, than more identical than preferentially with third speed, can provide respectively two kinds of velocity ratios thus on the first output shaft 521 and the second output shaft 522.
In sum, double-shaft clutch device provided by the utility model can be realized power failure-free gear shift.In addition, double-shaft clutch device provided by the utility model produces the power output of two kinds of friction speed ratios therein on an output shaft, when this engaging and disengaging gear and speed changer combination, can realize doubly shelves to the gear number of corresponding shaft in speed changer, can realize by the less number of gears more gear, to obtain better power performance, higher transmission efficiency, lower energy consumption, lower exhaust emissions, can realize power failure-free gear shift, and can transmission assembly be done relatively littlely, more economical, simpler.
As shown in Figure 4, Fig. 4 for according to the utility model the 4th embodiment for being integrated in the structural representation of the torsion damping mechanism on above-mentioned clutch.In the utility model, further integrated torsional damper mechanism 7 in above-mentioned clutch.In the present embodiment, this torsion damping mechanism 7 mainly comprises the first rotatable parts 71, the second rotatable parts 72 and spring cushion 73.Wherein, the first rotatable parts 71 and the second rotatable parts 72 coaxially arrange, and can relatively rotate.Between the first rotatable parts 71 and the second rotatable parts 72, form an annular housing, and spring cushion 73 is for to be arranged at the curved spring in this annular housing, and be connected the first rotatable parts 71 and the second rotatable parts 72 along the sense of rotation elasticity of the first rotatable parts 71 and the second rotatable parts 72.Preferably, this curved spring is in series by the spring of at least two different elasticity coefficient, improves thus effectiveness in vibration suppression.
In other embodiments, can circumferentially be symmetrically formed a plurality of spring card slots (not shown) separately in edge respectively at the first rotatable parts 71 and the second rotatable parts 72, now 73 of spring cushions comprise a plurality of straight shape spring (not shown) being placed in respectively in spring card slot.Equally preferably, in every group of corresponding spring card slot, comprise at least two series connection or the nested mutually different straight shape spring of elasticity coefficient.
In the present embodiment, torsion damping mechanism 7 can be integrated on any rotatable parts of the double-shaft clutch device shown in Fig. 1,2,3, one or more such as braked part that is preferably integrated in gear ring or the first clutch mechanism etc. on.For example, when torsion damping mechanism 7 is integrated on gear ring, the first rotatable parts 71 are directly connected with input shaft with in the second rotatable parts 72 one, and are provided with internal tooth on another in the first rotatable parts 71 and the second rotatable parts 72, and then carry out interior engagement with planetary gear set.When torsion damping mechanism 7 is integrated on braked part, the first rotatable parts 71 are directly connected with sun gear with in the second rotatable parts 72 one, and brake component is braked another in the first rotatable parts 71 and the second rotatable parts 72.It should be noted that torsion damping mechanism 7 can be integrated in gear ring and braked part simultaneously, respectively at gear ring and the first torsion damping mechanism and the second torsion damping mechanism that arrange on braked part with description scheme is identical above.Realize thus secondary vibration damping.In the present embodiment, driven member and the one or more of sun gear that torsion damping mechanism 7 also can be integrated in planet carrier, each clutch mechanism go up, and realize thus multistage vibration damping.Certainly, gear ring and braked part 1 are preferred.
Because the rotating speed from motor to automotive transmission and torque are periodically constantly to change, the torsional vibration that this can make power train produce; Because automobile running is on uneven road, make automotive transmission occur that angular velocity changes suddenly on the other hand, also can cause torsional vibration.These torsional vibrations all can, to impacting property of Parts for Power Train load, make its lost of life, even part of damage.The utility model, by integrated torsional damper mechanism on gear-doubling clutch device, can be eliminated torsional vibration and avoid resonance, prevents power train overload, therefore can one the individual components multiple function such as integrated " clutch ", " doubly grade " and " vibration damping " simultaneously.
Further, because torsion damping mechanism adopts two rotatable parts structures and has certain mass, therefore by calculating and configure the quality of the two, can realize the function identical with double mass flywheel, and then further integrated " double mass flywheel " function.
As shown in Figure 5, Fig. 5 is according to the schematic diagram of the selector in the utility model the 5th embodiment's speed changer and the gear relations of distribution.
In the present embodiment, speed changer for example comprises a plurality of shifting gear D1, D2, D3, D4, D5 and R and a plurality of selector X1, X2 switching before above-mentioned shifting gear, X3(, the combination of above-described stepper motor and clutch collar).Wherein, shifting gear D1, D2, D3, D4, D5 are respectively a grade to five grades of vehicle, and its gear ratio rises successively, and shifting gear R is reverse gear.In existing design, the shifting gear of adjacent gear (for example, one grade of corresponding shifting gear D1 and shifting gear D2 corresponding to second gear) use identical selector, therefore from one grade, shifting gears to the process of second gear, the shifting gear D1 that corresponding selector is first corresponding with one grade is separated, the shifting gear D2 corresponding with second gear engages again, extended the gearshift time, also may cause power interruption.In the present embodiment, the shifting gear of adjacent gear is used different selectors.Specifically, one grade of corresponding shifting gear D1 and shifting gear D4 corresponding to fourth gear are used same selector X1, the shifting gear D2 that second gear is corresponding and five grades of corresponding shifting gear D5 are used same selector X2, and corresponding shifting gear D3 and shifting gear R corresponding to reverse gear of third gear used same selector X3.Like this, when changing to second gear from one grade, when selector X1 is separated with shifting gear D1, selector X2 just can engage by shifting gear D2, has saved the gearshift time, can not produce power interruption, has improved shift quality.
In the above-described embodiments, only the utility model has been carried out to exemplary description, but those skilled in the art can carry out various modifications to the utility model after reading present patent application in the situation that not departing from spirit and scope of the present utility model.
Claims (9)
1. a double-shaft clutch device, is characterized in that, described double-shaft clutch device is connected between engine output shaft and transmission input shaft as individual components, and described double-shaft clutch device comprises:
Input shaft, for receiving input power;
Planetary body, described planetary body comprises power input component, driving component, transmission control member and power output member, wherein said power input component connects described input shaft;
The first output shaft, for connecting described power output member;
The first clutch mechanism, brakes described transmission control member for selectivity, so that described input shaft drives described the first output shaft through described driving component with First Speed ratio;
The second output shaft, coaxially arranges with described the first output shaft; And
The second clutch mechanism, engages described input shaft and described the second output shaft for selectivity, so that described input shaft drives described the second output shaft with second speed ratio without described driving component in the situation that;
Described double-shaft clutch device is further integrated with torsion damping mechanism, and described torsion damping mechanism comprises coaxial setting and the first rotatable parts and the second rotatable parts and the spring cushion that is connected described the first rotatable parts and described the second rotatable parts along the sense of rotation elasticity of described the first rotatable parts and described the second rotatable parts in relative rotation.
2. double-shaft clutch device as claimed in claim 1, it is characterized in that: between described the first rotatable parts and described the second rotatable parts, form an annular housing, described spring cushion is the curved spring being arranged in described annular housing, or described the first rotatable parts and described the second rotatable parts are respectively along being circumferentially symmetrically formed a plurality of spring card slots separately, and described spring cushion comprises a plurality of straight shape spring being placed in respectively in described spring card slot.
3. double-shaft clutch device as claimed in claim 2, it is characterized in that: described curved spring is in series by the spring of at least two different elasticity coefficient, or in every group of corresponding described spring card slot, comprise at least two series connection or the nested mutually different described straight shape spring of elasticity coefficient.
4. double-shaft clutch device according to claim 1, it is characterized in that: described double-shaft clutch device further comprises the 3rd clutch mechanism, for selectivity, engage described input shaft and described the first output shaft, so that described input shaft drives described the first output shaft with third speed ratio without described driving component in the situation that.
5. double-shaft clutch device according to claim 4, it is characterized in that: described double-shaft clutch device further comprises the 4th clutch mechanism and the 5th clutch mechanism, described the 3rd clutch mechanism selectivity engages described input shaft and described power output member, described the 4th clutch mechanism selectivity engages described power output member and described the first output shaft, described the 5th clutch mechanism selectivity engages described power output member and described the second output shaft, wherein said the 4th clutch mechanism and described the first clutch mechanism coordinate with described First Speed than driving described the first output shaft, described the 4th clutch mechanism coordinates with described the 3rd clutch mechanism with described third speed than driving described the first output shaft, described the 5th clutch mechanism coordinates with described the first clutch mechanism with the 4th speed than driving described the second output shaft.
6. double-shaft clutch device as claimed in claim 1, it is characterized in that: described planetary body comprises sun gear, be arranged at described sun gear around and with the planetary gear set of described sun gear outer gearing, with the gear ring meshing in described planetary gear set and be arranged at the planet carrier in described planetary gear set, described power input component is described gear ring, described power output member is described planet carrier, described transmission control member is described sun gear, described torsion damping mechanism comprises the first torsion damping mechanism being integrated on described gear ring, the first rotatable parts of wherein said the first torsion damping mechanism are connected with described input shaft with in the second rotatable parts one, the first rotatable parts of described the first torsion damping mechanism and another in the second rotatable parts are provided with internal tooth, and with described planetary gear set in mesh.
7. double-shaft clutch device as claimed in claim 1, it is characterized in that: described planetary body comprises sun gear, be arranged at described sun gear around and with the planetary gear set of described sun gear outer gearing, with the gear ring meshing in described planetary gear set and be arranged at the planet carrier in described planetary gear set, described power input component is described gear ring, described power output member is described planet carrier, described transmission control member is described sun gear, described the first clutch mechanism comprises braked part and the brake component for described braked part is braked with the coaxial setting of described sun gear, described torsion damping mechanism comprises the second torsion damping mechanism being integrated on described braked part, the first rotatable parts of wherein said the second torsion damping mechanism are connected with described sun gear with in the second rotatable parts one, described brake component is braked another in the first rotatable parts of described the second torsion damping mechanism and the second rotatable parts.
8. a vehicle speed variation assembly, is characterized in that, described vehicle speed variation assembly comprise double-shaft clutch device as described in claim 1-7 any one and with as described in the speed changer that is connected of double-shaft clutch device.
9. vehicle speed variation assembly as claimed in claim 8, is characterized in that: described speed changer comprises a plurality of shifting gears and the selector switching between described a plurality of shifting gears, and wherein the shifting gear of adjacent gear is used different selectors.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320709247.1U CN203906678U (en) | 2013-11-11 | 2013-11-11 | Double-shaft clutch device and vehicle speed change assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320709247.1U CN203906678U (en) | 2013-11-11 | 2013-11-11 | Double-shaft clutch device and vehicle speed change assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203906678U true CN203906678U (en) | 2014-10-29 |
Family
ID=51780959
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320709247.1U Withdrawn - After Issue CN203906678U (en) | 2013-11-11 | 2013-11-11 | Double-shaft clutch device and vehicle speed change assembly |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203906678U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN106763572A (en) * | 2016-11-30 | 2017-05-31 | 龚小娥 | A kind of triple axle clutch speed variator |
| CN106763571A (en) * | 2016-11-30 | 2017-05-31 | 龚小娥 | A kind of triple axle clutch speed variator |
| CN106838155A (en) * | 2016-11-30 | 2017-06-13 | 龚小娥 | A kind of triple axle clutch speed variator |
-
2013
- 2013-11-11 CN CN201320709247.1U patent/CN203906678U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN106763572A (en) * | 2016-11-30 | 2017-05-31 | 龚小娥 | A kind of triple axle clutch speed variator |
| CN106763571A (en) * | 2016-11-30 | 2017-05-31 | 龚小娥 | A kind of triple axle clutch speed variator |
| CN106838155A (en) * | 2016-11-30 | 2017-06-13 | 龚小娥 | A kind of triple axle clutch speed variator |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20141029 Effective date of abandoning: 20170412 |