CN203730654U - Dual-mass flywheel and automobile comprising dual-mass flywheel - Google Patents
Dual-mass flywheel and automobile comprising dual-mass flywheel Download PDFInfo
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- CN203730654U CN203730654U CN201320838900.4U CN201320838900U CN203730654U CN 203730654 U CN203730654 U CN 203730654U CN 201320838900 U CN201320838900 U CN 201320838900U CN 203730654 U CN203730654 U CN 203730654U
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- mass flywheel
- flange
- double
- rotating speed
- flywheel
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Abstract
The utility model relates to a dual-mass flywheel which comprises a first mass flywheel body, a second mass flywheel body, a flange and a torsion damper. The flange and the torsion damper are located between the first mass flywheel body and the second mass flywheel body. The first mass flywheel body is fixed to the flange on the second mass flywheel body under the drive of the torsion damper so as to drive the flange of the second mass flywheel body to rotate. The dual-mass flywheel further comprises a flange locking structure, according to the flange locking structure, when the rotating speed of the first mass flywheel body is lower than the preset rotating speed, the first mass flywheel body and the flange are locked together, and when the rotating speed of the first mass flywheel body is higher than the preset rotating speed, the first mass flywheel body is disengaged from the flange. The utility model further relates to an automobile comprising the dual-mass flywheel.
Description
Technical field
The automobile that the application relates to a kind of double mass flywheel and comprises this double mass flywheel.
Background technique
Double mass flywheel vibration damper in automobile mainly comprises the first mass flywheel that is arranged at motor car engine one side, be arranged at the second mass flywheel of speed changer one side and be arranged at the first mass flywheel and the second mass flywheel between torsional vibration damper.Compared with clutch damper, double mass flywheel vibration damper can reduce the natural frequency of motor and speed changer vibration system, to avoid the resonance when the auto idle speed rotating speed.
Conventionally, use double mass flywheel can make the point of resonance of automobile clutch vibration damping be reduced to 450r/min left and right from 1200r/min left and right.The point of resonance of double mass flywheel has been avoided conventional speed range, but in the time that the resonance of 450r/min can make client in vehicle ignition, feels and have influence on client's comfort by the noise that resonance produces, and causes client's complaint.
Model utility content
The utility model main purpose is to provide a kind of double mass flywheel of structure of improvement that has, and the technical problem of resonance occurs when the engine ignition operating mode to solve automobile.
For this reason, according to a model utility of the present utility model, a kind of double mass flywheel is provided, comprise the first mass flywheel, the second mass flywheel and flange and torsional vibration damper between described the first mass flywheel and described the second mass flywheel, described the first mass flywheel drives the flange being fixed on described the second mass flywheel by described torsional vibration damper, thereby drive described the second quality flange to rotate, wherein, described double mass flywheel also comprises flange keying structure, described flange keying structure is configured to, when the rotating speed of described the first mass flywheel locks together described the first mass flywheel and described flange during lower than desired speed, and when the rotating speed of described the first mass flywheel goes out of lock described the first mass flywheel and described flange during higher than desired speed.
According to preferred implementation, when the rotating speed of described the first mass flywheel is during lower than desired speed, described flange keying structure utilizes mechanical hook to make a concerted effort or frictional force or magnetic attracting force lock together described the first mass flywheel and described flange.
According to preferred implementation, described flange keying structure comprises the rotating shaft of being fixed on one of described the first mass flywheel or flange, and be sleeved on snap and the latch hook in described rotating shaft, when the rotating speed of described the first mass flywheel is during lower than desired speed, described latch hook makes described the first mass flywheel and described flange lock together under the active force of described snap, and when the rotating speed of described the first mass flywheel is during higher than desired speed, the centrifugal force of described latch hook overcomes the active force of described snap and is thrown away, and described the first mass flywheel and described flange are gone out of lock.
According to preferred implementation, the quality of described latch hook is between 0.2～0.3kg, and the rigidity of described snap is within the scope of 4Nm/ °～6Nm/ °, or, the quality of described latch hook is between 0.2～0.3kg, and the rigidity of described snap is within the scope of 3.8Nm/ °～5.8Nm/ °.
According to preferred implementation, described rotating shaft is formed the part of one of described the first mass flywheel or flange, or forms discretely and be mechanically fixed to one of described the first mass flywheel or flange with one of described the first mass flywheel or flange.
According to preferred implementation, another in described the first mass flywheel or flange is formed the hooked part coordinating with described latch hook.Described hooked part is projection or the recess being formed on another in described the first mass flywheel or flange, or attaches to the appendix on another in described the first mass flywheel or flange.
According to preferred implementation, described flange keying structure comprises the latch being fixed on one of described the first mass flywheel or flange, another in described the first mass flywheel or flange comprises the locking surface cooperating with described latch, when the rotating speed of described the first mass flywheel is during lower than desired speed, utilize the frictional force between described latch and described locking surface that described the first mass flywheel and described flange are locked together, and when the rotating speed of described the first mass flywheel is during higher than desired speed, the centrifugal force of described latch overcomes described frictional force, and described the first mass flywheel and described flange are gone out of lock.
According to preferred implementation, described double mass flywheel comprises one or along equally distributed two or more flange keying structures of circumferencial direction.
According to preferred implementation, described desired speed is about 500r/min.
According on the other hand of the present utility model, a kind of automobile is also provided, comprise double mass flywheel as above, wherein, the first mass flywheel of described double mass flywheel is fixed together with the engine output shaft of automobile, and the second mass flywheel of described double mass flywheel is fixed together with the clutch of automobile.
Be provided with flange keying structure according to double mass flywheel of the present utility model, make in the time of automotive ignition process, the first mass flywheel of double mass flywheel can keep locking with flange.Once motor completes igniting, rotating speed has exceeded point of resonance, and the locking of the first mass flywheel and flange is thrown off, double mass flywheel enters normal vibration damping working state, so effectively avoid the point of resonance of transmission system, reduced noise in igniting process, improved the travelling comfort of passenger.
Brief description of the drawings:
The application's above-mentioned feature and further feature and advantage will be better understood in the embodiment who describe with reference to the accompanying drawings below.Wherein:
Fig. 1 shows according to the stereogram of the double mass flywheel of the utility model preferred embodiment, and wherein, the second mass flywheel is not shown.
Fig. 2 shows the end view drawing of analysing and observe of double mass flywheel in Fig. 1, has wherein excised the halfbody of double mass flywheel.
Fig. 3 shows the stereogram of the first mass flywheel with good grounds flange keying structure of the present utility model.
Fig. 4 amplifies the flange keying structure part showing in Fig. 3.
Embodiment
Should be appreciated that, will describe according to the preferred implementation of the double mass flywheel of principle of the present utility model below.Shown in figure is only illustrative exemplary type preferred embodiment, is not intended to limit protection domain of the present utility model.
With reference to Fig. 1-2, comprise the first mass flywheel 20, the second mass flywheel (not shown) and the torsional vibration damper 60 between the first mass flywheel 20 and the second mass flywheel and flange 70 according to the double mass flywheel 100 of the utility model preferred embodiment.Wherein, the first mass flywheel 20 that is installed on the double mass flywheel 100 in automobile is connected with motor car engine output shaft (not shown), and the second mass flywheel is connected with speed changer (not shown).The moment of torsion rotating speed of motor car engine output shaft output is passed to the second mass flywheel by torsional vibration damper 60 and flange 70, and therefore drive speed transmission work.
Torsional vibration damper 60 is configured to comprise arc spring 64, and because the radius of arc spring 64 is larger, it allows larger torsion angle.Preferably, arc spring 64 comprises interior spring and outer spring.The number of arc spring 64 can be selected as required.In illustrated embodiment, be provided with two arc springs 64.
The first mass flywheel 20 comprises dish type body 30, ring part 40, dish type body 30 facing to the side of the second mass flywheel on projection annular protrusion 50 out, and be positioned at the hub portion 22 at center.
The dish type body 30 of the first mass flywheel 20, annular protrusion 50 and ring part 40 limit the annular pass 24 for arc spring 64, are arranged in described annular pass 24 for the guiding groove 62 of the arc spring 64 that leads.
Annular pass 24 and the second not shown mass flywheel limit the annular space of the sealing of accommodating torsional vibration damper 60.Torsional vibration damper 60 can also comprise the viscous grease in the annular space that is filled to this sealing, and described viscous grease, except damping function is provided, can also alleviate the wearing and tearing to arc spring 64.
The first mass flywheel 20 also comprises from the limited part 42 of the inside projection of inner peripheral surface of ring part 40, for guiding groove 62 being provided to circumferential backstop action and to arc spring 64 transmitting torques.
Flange 70 comprises dish type body 72 and the protruding pinna 74 from the outside projection of dish type body.Thereby being placed on the protruding pinna 74 that arc spring 64 in the first mass flywheel 20 acts on flange 70 drives flange 70 to rotate.
Pass through said structure, when the first mass flywheel 20 is driven and is rotated, the limited part 42 of the first mass flywheel 20 compresses arc spring 64 makes its torsional deflection, the protruding pinna 74 that arc spring 64 acts on flange 70 promotes flange 70 and rotates, and the second mass flywheel being therefore fixed together with flange 70 is rotated.
By means of the torsional vibration damper 60 being made up of arc spring 64 and viscous grease, double mass flywheel 100 has been realized the function of transmitting torque and vibration damping, makes the point of resonance of automobile clutch vibration damping be reduced to 450r/min left and right from 1200r/min left and right.The point of resonance of double mass flywheel has been avoided conventional speed range.
Also comprise flange keying structure according to double mass flywheel 100 of the present utility model.
On the one hand, described flange keying structure locks together flange 70 and the first mass flywheel 20 while being configured to rotating speed when the first mass flywheel 20 lower than a certain desired speed, in this case, arc spring 64 is not compressed, the first mass flywheel 20 directly drives flange 70 to rotate, the rigidity of whole system is very large, and resonance speed is very high.
On the other hand, described flange keying structure goes out of lock flange 70 and the first mass flywheel 20 while being configured to when the rotating speed arrival of the first mass flywheel 20 or higher than this desired speed, and the first mass flywheel 20 drives flange 70 to rotate by torsional vibration damper 60 again.
The setting of described flange keying structure can make double mass flywheel 100 successfully avoid the resonance phenomenon in the time of 400r/min-500r/min rotating speed, reduces the noise that resonance produces, and improves the travelling comfort of passenger.
Particularly preferably, described desired speed is set to about 500r/min.
Root above-mentioned principle of the present utility model, described flange keying structure can be realized by any concrete structure, can be arranged on as shown in the figure on the first mass flywheel 20, also can be arranged on any other parts or any other position, as long as can realize above-mentioned functions, being for example arranged at is also possible on flange 70.
As an example of flange keying structure has been shown in Fig. 1-4, hook together structure 80.
The described structure 80 that hooks together comprises the rotating shaft 82 in the annular protrusion 50 that is fixed on the first mass flywheel 20, is sleeved on the snap 84 in rotating shaft 82, and is connected to the latch hook 86 of snap 84 one end.
When the rotating speed of the first mass flywheel 20 is lower than desired speed for example when 500r/min, latch hook 86 is hooked on flange 70 under the pretightening force effect of snap 84, and flange 70 and the first mass flywheel 20 are locked together; During when the rotating speed arrival of the first mass flywheel 20 or higher than this desired speed, latch hook 86 overcomes the power of snap 84 and 82 rotates around the shaft under the effect of centrifugal force, thereby disengaging is sealed with flange 70, locking between flange 70 and the first mass flywheel 20 is unlocked, and the first mass flywheel 20 drives flange 70 to rotate by torsional vibration damper 60 afterwards.
Those skilled in the art should be appreciated that, for achieving the above object, the snap 84 of any type can be used.For example, in diagram, snap 84 is torsion spring.
Preferably, torsion spring 84 is not changeless to the force value of latch hook 86.The rigidity of torsion spring 84 and mounting point preferably meet following requirement: in the time that the first mass flywheel 20 starts to rotate, the active force maximum of torsion spring 84 to latch hook 86, make latch hook 86 can guarantee to hook together securely flange 70, namely make together with flange 70 guarantees secure lock with the first mass flywheel 20; Along with the increase of the first mass flywheel 20 rotating speeds, the centrifugal force that latch hook 86 is subject to increases gradually, and snap 84 preferably reduces gradually to the active force of latch hook 86; When the rotating speed of the first mass flywheel 20 arrives desired speed for example when 500r/min, thereby the centrifugal force that latch hook 86 is subject to increases to and is enough to overcome snap 84 and the active force of latch hook 86 is arrived to the effect being thrown out of.
That is to say, in the time that needs keep locking, the force value maximum of torsion spring to latch hook, to ensure the effect of locking; Along with the rotating speed of the first mass flywheel raises, power value be decline trend, ensured the effect that latch hook is thrown away; When treating again locking, the power value of torsion spring presents the trend of rising, and it is a progressive process that hooking together of latch hook 86 operated, and has prevented because of the impact of the unexpected locking of latch hook to flange.
Hooking together structure and needn't be limited to the concrete structure shown in diagram as flange keying structure.For example rotating shaft 82 arbitrarily mode be attached to the first mass flywheel 20, for example, by known method in related domains such as welding, be threaded.Alternatively, rotating shaft 82 can be and the structure of the first mass flywheel 20 one.The position of rotating shaft 82 on the first mass flywheel 20 hook together the position of structure 80 and also can arrange according to specific design, as long as can meet above-mentioned functions.
Flange 70 is hooked together the position that structure 80 hooks together and also can be determined according to specific needs.For example, flange 70 shown in figure has been formed recess, hooks together for the latch hook 86 that is hooked together structure 80.Selectively, latch hook 86 can hook together the outer circumference of flange 70, or can hook together any extention that is attached to flange 70, for example, be attached to hook, ring etc. on flange 70.
Alternately, hook together structure 80 and can be arranged on flange 70, for arbitrary part of the first mass flywheel 20 or attached any additional structure hook thereon.
According to double mass flywheel of the present utility model, by flange keying structure is set, make in the time of automotive ignition process, the first mass flywheel of double mass flywheel can keep locking with flange, thus the arc shock-absorbing spring of double mass flywheel is inoperative.Once motor completes igniting, rotating speed has exceeded point of resonance, the locking of the first mass flywheel and flange is thrown off, and the first mass flywheel of double mass flywheel drives flange and the second mass flywheel by torsional vibration damper, and double mass flywheel enters normal vibration damping working state.The point of resonance that this has avoided transmission system effectively, has reduced noise in igniting process, improves the travelling comfort of passenger.
In addition, adopt and hook together structure 80 as flange keying structure, simple in structure, locking is effective, does not affect the effectiveness in vibration suppression of the double mass flywheel under other operating modes simultaneously.Preferably, consider the compactedness of structural configuration, the quality of locking hook is between 0.2～0.3kg.The rigidity of torsion spring depends on the specification of double mass flywheel and the quality of locking hook.For example, according to the quality of locking hook, for the double mass flywheel of 240 specifications, the torsion spring stiffness of keying structure is preferably within the scope of 4Nm/ °～6Nm/ °; For the double mass flywheel of 228 specifications.The torsion spring stiffness of keying structure is preferably within the scope of 3.8Nm/ °～5.8Nm/ °.
Hook together structure 80 except illustrated, other structure that can ensure in good time locking and in good time separating effect can be used.For example, in optional embodiment, adopt friction structure or magnetic attraction structure as flange keying structure.Particularly, for example, the frictional force that utilization is fixed between latch and the flanged surface on the first mass flywheel keeps the first mass flywheel and flange locking, when the rotating speed of the first mass flywheel is during higher than 500r/min for example, the centrifugal force overcome friction that latch is subject to, make flange and the first mass flywheel depart from locking, double mass flywheel enters conventional vibration reducing mode.The shock effect that this structure both can avoid the locking that hooks together structure to bring, can avoid again slotting on flange or the first mass flywheel etc.
While selecting flange keying structure, preferable shape is simple, the structure of compact structure, avoids arranging and impacting to the space of double mass flywheel.
The quantity of flange keying structure and position can be considered according to concrete design, generally can select the middle-end of design on the first quality both sides, can ensure like this effect of locking, can not affect again the position of miscellaneous part.
Be mainly used according to double mass flywheel of the present utility model, but be not limited only to, automotive field.For example, between motor and speed changer for automobile, realize the function that reduces the natural frequency of motor and speed changer vibration system and avoid producing resonance in the time of idling speed.
The utility model have been described in detail about preferred illustrated embodiment.But all descriptions are only used for describing, and should not be construed as model utility form is carried out to any restriction.In the situation that not departing from spirit and scope of the present utility model, those of ordinary skill in the art can also make various distortion and improvement.Therefore, all technological schemes that are equal to all should belong to category of the present utility model also by every claim of the present utility model is limited.
Claims (10)
1. a double mass flywheel, it is characterized in that, comprise the first mass flywheel, the second mass flywheel and flange and torsional vibration damper between described the first mass flywheel and described the second mass flywheel, described the first mass flywheel drives the flange being fixed on described the second mass flywheel by described torsional vibration damper, thereby drive described the second quality flange to rotate
Wherein, described double mass flywheel also comprises flange keying structure, described flange keying structure is configured to, when the rotating speed of described the first mass flywheel locks together described the first mass flywheel and described flange during lower than desired speed, and described the first mass flywheel and described flange are gone out of lock during higher than desired speed when the rotating speed of described the first mass flywheel.
2. double mass flywheel according to claim 1, it is characterized in that, when the rotating speed of described the first mass flywheel is during lower than desired speed, described flange keying structure utilizes mechanical hook to make a concerted effort or frictional force or magnetic attracting force lock together described the first mass flywheel and described flange.
3. double mass flywheel according to claim 2, is characterized in that, described flange keying structure comprises the rotating shaft of being fixed on one of described the first mass flywheel or flange, and is sleeved on snap and latch hook in described rotating shaft,
When the rotating speed of described the first mass flywheel is during lower than desired speed, described latch hook makes described the first mass flywheel and described flange lock together under the active force of described snap, and when the rotating speed of described the first mass flywheel is during higher than desired speed, the centrifugal force of described latch hook overcomes the active force of described snap to be thrown away, and described the first mass flywheel and described flange are gone out of lock.
4. double mass flywheel according to claim 3, it is characterized in that, the quality of described latch hook is between 0.2～0.3kg, and the rigidity of described snap is within the scope of 4Nm/ °～6Nm/ °, or, the quality of described latch hook is between 0.2～0.3kg, and the rigidity of described snap is within the scope of 3.8Nm/ °～5.8Nm/ °.
5. double mass flywheel according to claim 3, it is characterized in that, described rotating shaft is formed the part of one of described the first mass flywheel or flange, or forms discretely and be mechanically fixed to one of described the first mass flywheel or flange with one of described the first mass flywheel or flange.
6. double mass flywheel according to claim 3, it is characterized in that, another in described the first mass flywheel or flange is formed the hooked part coordinating with described latch hook, described hooked part is projection or the recess being formed on another in described the first mass flywheel or flange, or attaches to the appendix on another in described the first mass flywheel or flange.
7. double mass flywheel according to claim 2, it is characterized in that, described flange keying structure comprises the latch being fixed on one of described the first mass flywheel or flange, and another in described the first mass flywheel or flange comprises the locking surface cooperating with described latch
When the rotating speed of described the first mass flywheel is during lower than desired speed, utilize the frictional force between described latch and described locking surface that described the first mass flywheel and described flange are locked together, and when the rotating speed of described the first mass flywheel is during higher than desired speed, the centrifugal force of described latch overcomes described frictional force, and described the first mass flywheel and described flange are gone out of lock.
8. according to arbitrary described double mass flywheel in claim 1-7, it is characterized in that, described double mass flywheel comprises one or along equally distributed two or more flange keying structures of circumferencial direction.
9. according to arbitrary described double mass flywheel in claim 1-7, it is characterized in that, described desired speed is about 500r/min.
10. an automobile, it is characterized in that, comprise according to arbitrary described double mass flywheel in claim 1-9, the first mass flywheel of described double mass flywheel is fixed together with the engine output shaft of automobile, and the second mass flywheel of described double mass flywheel is fixed together with the clutch of automobile.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320838900.4U CN203730654U (en) | 2013-12-18 | 2013-12-18 | Dual-mass flywheel and automobile comprising dual-mass flywheel |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320838900.4U CN203730654U (en) | 2013-12-18 | 2013-12-18 | Dual-mass flywheel and automobile comprising dual-mass flywheel |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203730654U true CN203730654U (en) | 2014-07-23 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320838900.4U Expired - Fee Related CN203730654U (en) | 2013-12-18 | 2013-12-18 | Dual-mass flywheel and automobile comprising dual-mass flywheel |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203730654U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106704480A (en) * | 2015-07-20 | 2017-05-24 | 比亚迪股份有限公司 | Dual mass flywheel |
| CN111065174A (en) * | 2019-12-31 | 2020-04-24 | 东风汽车集团有限公司 | Dual-mass flywheel heating device and transmission system with same |
-
2013
- 2013-12-18 CN CN201320838900.4U patent/CN203730654U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106704480A (en) * | 2015-07-20 | 2017-05-24 | 比亚迪股份有限公司 | Dual mass flywheel |
| CN111065174A (en) * | 2019-12-31 | 2020-04-24 | 东风汽车集团有限公司 | Dual-mass flywheel heating device and transmission system with same |
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| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140723 Termination date: 20211218 |
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| CF01 | Termination of patent right due to non-payment of annual fee |