CN205064694U - Bent axle torsional damper - Google Patents
Bent axle torsional damper Download PDFInfo
- Publication number
- CN205064694U CN205064694U CN201520596942.0U CN201520596942U CN205064694U CN 205064694 U CN205064694 U CN 205064694U CN 201520596942 U CN201520596942 U CN 201520596942U CN 205064694 U CN205064694 U CN 205064694U
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- vibration damper
- damper
- flange
- hub
- permanent magnets
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Abstract
The utility model aims at providing a simple structure, stable performance, longe -lived bent axle torsional damper contain a shock absorber wheel hub, the shock absorber flange of suit on shock absorber wheel hub rotatably, and shock absorber wheel hub has a central line, and shock absorber wheel hub and shock absorber flange have perpendicular to central line and the inboard relative with the other side respectively, its characterized in that, shock absorber wheel hub's inboard is provided with the first permanent magnetism body group that contains at least a pair of N, S polarity permanent magnet, the inboard of shock absorber flange is provided with the second permanent magnetism body group that contains at least a pair of N, S polarity permanent magnet, when quiescent condition, permanent magnet in first permanent magnetism body group and the second permanent magnetism body group two double -phase to, and relative permanent magnet polarity opposite.
Description
Technical field
The utility model relates to a kind of crankshaft tortional vibration damper for motor vehicle engine crankshaft end.
Background technique
With on the motor vehicle of petrol engine or diesel engine powers, when motor runs, whole axle system can produce torsional vibration, this vibration can affect the comfort level of vehicle ride greatly, even also can affect the operation of whole Power output and transmission system, time serious, once resonate, to Analyse for Cracking of Engine Crankshaft be caused, thus serious accident will occur.Therefore, what engine torque was vibrated alleviates and eliminate is the major issue that engine shaft system designer needs to consider.
Along with technical development, the torsional vibration damper of crankshaft end has been widely used on motor.Existing a kind of crankshaft tortional vibration damper adopts rubber ring vibration damping, belt pulley is bonded on wheel hub by vibration isolation rubber circle, when the engine is running, vibration isolation rubber circle produces deformation, be heat energy by the Conversion of Energy of torsional vibration, thus the torsional oscillation intensity of abatement engine shaft system, reduction torsional oscillation amplitude, reach the object of torsion damping; Further, by changing the rotary inertia of belt pulley and the rigidity of vibration isolation rubber, the natural frequency of vibration and the oscillatory type of whole axle system can be regulated.But after a period of time service time, vibration isolation rubber circle heat ageing, its effectiveness in vibration suppression will weaken greatly, if change not in time, crankshaft wear will be caused to aggravate, and total noise of centrifuge increases, and even produce resonance and cause crankshaft breakdown generation security incident.
Summary of the invention
The crankshaft tortional vibration damper that the purpose of this utility model is to provide that a kind of structure is simple, stable performance, life-span are long, the defect existed with the torsional vibration damper overcoming prior art.
For achieving the above object, crankshaft tortional vibration damper of the present utility model comprises: a damper hub, one is rotatably sleeved on the vibration damper flange on damper hub, damper hub has a center line, damper hub has inner side perpendicular to center line and relative with the other side respectively with vibration damper flange, it is characterized in that, the inner side of damper hub is provided with and comprises at least one pair of N, first set of permanent magnets of S polarity permanent magnet, the inner side of vibration damper flange is provided with and comprises at least one pair of N, second set of permanent magnets of S polarity permanent magnet, when state of rest, first set of permanent magnets is relative between two with the permanent magnet in the second set of permanent magnets, and relative permanent magnet polarity is contrary.
Further, gap is left between the magnet of the first set of permanent magnets and the second set of permanent magnets.
As an aspect of the present utility model, at least one limit stoper is provided with between damper hub and vibration damper flange, limit stoper comprises a kidney slot of the inner side being positioned at vibration damper flange further, and be positioned at inner side one protruding of damper hub, protruding stretches into kidney slot at least partially and can circumferentially move wherein.
Further, kidney slot size is circumferentially greater than protruding size circumferentially.
Further, projection is a rubber parts being connected in the inner side of damper hub.
Further, a crankshaft end flange is connected in the outside of damper hub.
Further, a belt pulley is connected in the outside of vibration damper flange, can with vibration damper flange Concentric rotation.
Further, belt pulley comprises the first belt grooves portion with the first outer diameter.
Further, belt pulley also comprises the second belt grooves portion with the second outer diameter, and the first outer diameter is less than the second outer diameter.
Further, a clutch shaft bearing, an inner spacing collar, one second bearing are sleeved on damper hub successively, and vibration damper flange is enclosed within the outer ring of the outer ring of clutch shaft bearing, an outer separator and the second bearing regularly.
By adopting crankshaft tortional vibration damper of the present utility model, crankshaft torsional vibrations cause two heteropole permanent magnets relative in two set of permanent magnets in vibration damper to produce circumferential relative displacement, the magnetic repulsion that the homopolarity permanent magnet on its magnetic attraction and side, opposite produces with it makes two set of permanent magnets small size opposing oscillatory in the circumferential all the time, just as spring, consume the energy of crankshaft torsional vibrations gradually, reach vibration damping object.And two relative set of permanent magnets are compared to the vibration damping components and parts of other materials, there is not the problem of material ageing, inefficacy, ensure that crankshaft tortional vibration damper stable performance of the present utility model, long service life.
Limit stoper then limits the position of heteropole permanent magnet relative in two set of permanent magnets, makes it there will not be circumferential displacement to cross the situation of position, ensures two set of permanent magnets relatively small size circuit oscillation all the time, can consume the energy of crankshaft torsional vibrations continuously.
When in vibration damper, two set of permanent magnets relatively rotate, leave gap between two set of permanent magnets and ensure that two assemblies directly can not come in contact friction, avoid the generation of noise and wearing and tearing, ensure that the quiet of crankshaft tortional vibration damper of the present utility model and the characteristic without wearing and tearing.
Accompanying drawing explanation
Do to describe further and set forth to the utility model below in conjunction with accompanying drawing.
Fig. 1 is the sectional view that the crankshaft tortional vibration damper of the first-selected mode of execution of the utility model is analysed and observe along a face through center line;
Fig. 2 is the sectional view that the crankshaft tortional vibration damper of first-selected mode of execution is analysed and observe along another face through center line;
Fig. 3 is the inner side figure of the damper hub of the crankshaft tortional vibration damper of first-selected mode of execution;
Fig. 4 is the inner side figure of the vibration damper flange of the crankshaft tortional vibration damper of first-selected mode of execution.
Embodiment
As Figure 1-4 be the crankshaft tortional vibration damper of first-selected mode of execution of the present utility model, comprise damper hub 1, vibration damper flange 2.Preferably, one clutch shaft bearing 11, inner spacing collar 12,1 second bearing 11 ' is set in damper hub 1 successively, and withstand on the shaft shoulder 1 ' of damper hub 1, vibration damper flange 2 is enclosed within the outer ring of the outer ring of clutch shaft bearing 11, outer separator 12 ', the second bearing 11 ', thus can rotate relative to the center line X of damper hub 1 around damper hub 1.One locking nut 13 is screwed in damper hub 1 and installs on the end 14 of clutch shaft bearing, inner spacing collar, outer separator, the second bearing, between locking nut 13 and clutch shaft bearing 11, is also provided with dust cover 15, first interstage sleeve 16 successively.One jump ring 21 is contained in the groove of the inner peripheral surface of vibration damper flange 2, between jump ring 21 and the outer ring of clutch shaft bearing 11, be also provided with the second interstage sleeve 16 '.First seal ring 17 and the second seal ring 17 ' are separately positioned between clutch shaft bearing 11 and jump ring 21 and between the second bearing 11 ' and vibration damper flange 2.Preferably, between the first seal ring 17 and clutch shaft bearing 11, between clutch shaft bearing 11 and the second bearing 11 ', fill lubricant grease respectively between the second bearing 11 ' and the second seal ring 17 '.
On the direction perpendicular to center line X, the both sides that vibration damper wheel hub 1 is relative with both vibration damper flanges 2 are inner side, are referred to as the inner side of the inner side of damper hub, vibration damper flange; On the other sidely be respectively the outside of damper hub, the outside of vibration damper flange.
Preferably, a belt pulley 3 is enclosed within the outer circumferential face in the outside of vibration damper flange 2, and is fixedly connected to vibration damper flange 2 by screw 31.Belt pulley 3 comprises one first belt grooves portion 32 and the second belt grooves portion 32 of belt grooves portion 33, first has the first outer diameter, and the second belt grooves portion 33 has the second outer diameter, and wherein the first outer diameter is less than the second outer diameter.
Preferably, in the outside of damper hub 1, a crankshaft end flange 4 is permanently connected by screw 41 and damper hub.Crankshaft end flange 4 is connected with engine crankshaft by screw 42.
Preferably, the inner side of damper hub 1 is circumferentially provided with one first set of permanent magnets 18, and the inner side of vibration damper flange 2 is circumferentially provided with one second set of permanent magnets 28.The permanent magnet quantity that first set of permanent magnets 18 and the second set of permanent magnets 28 comprise is equal, all comprises at least one pair of N, S polarity permanent magnet of arranging successively.When state of rest, the first set of permanent magnets 18 is relative between two with the permanent magnet in the second set of permanent magnets 28, and relative permanent magnet polarity is contrary.
As shown in Figure 3 be the inner side figure of damper hub in first-selected mode of execution, as shown in Figure 4 be the inner side figure of vibration damper flange in first-selected mode of execution.Preferably, the first set of permanent magnets and the second set of permanent magnets comprise 12 pairs of N, S polarity permanent magnets respectively, and in each set of permanent magnets 6 pairs of N, S polarity permanent magnets and other 6 pairs of N, S polarity permanent magnets head and the tail between leave a spacer segment.
When motor runs, crankshaft torsional vibrations cause two heteropole permanent magnets relative in two set of permanent magnets in vibration damper to produce circumferential relative displacement, the magnetic repulsion that the homopolarity permanent magnet on its magnetic attraction and side, opposite produces with it makes two set of permanent magnets small size opposing oscillatory in the circumferential all the time, just as spring, consume the energy of crankshaft torsional vibrations gradually, reach vibration damping object.
In order to make two relative heteropole permanent magnets be unlikely to swing position, and slightly can swing constantly as torque spring, between vibration damper flange 2 and damper hub 1, being also provided with at least one limit stoper.As shown in Figure 1 and Figure 4, preferably, multiple kidney slot 29 (in figure, number of elements sign shows one of them) is had in the inner side of vibration damper flange 2, multiple protruding 19 are correspondingly provided with in the inner side of damper hub 1, protruding 19 stretch at least partially in kidney slot 29, and can circumferentially move wherein.Preferably, protruding 19 is-rubber parts 191, and its inner ring has been permanently connected-backing metal 292, then is fixed to the inner side of damper hub 1 by a screw.Preferably, kidney slot 29 size is circumferentially greater than projection 19 size circumferentially.
Preferably, as shown in Figure 1, between the inner side of damper hub 1 and the inner side of vibration damper flange 2, leave gap, between the first set of permanent magnets 18 and the second set of permanent magnets 28, also leave gap, like this in vibration damping process, can slightly swing swimmingly between damper hub 1 and vibration damper flange 2.
Above-mentioned embodiment is only described preferred implementation of the present utility model, and not limits protection domain of the present utility model.Under the prerequisite not departing from the utility model design concept and scope; those of ordinary skill in the art to the various distortion done by the technical solution of the utility model, alternative and improvement, all should belong to protection category of the present utility model according to text description provided by the utility model, accompanying drawing.Protection domain of the present utility model is determined by claim.
Claims (10)
1. a crankshaft tortional vibration damper, comprise: a damper hub, one is rotatably sleeved on the vibration damper flange on described damper hub, described damper hub has a center line, described damper hub has inner side perpendicular to described center line and relative with the other side respectively with described vibration damper flange, it is characterized in that, the inner side of described damper hub is provided with and comprises at least one pair of N, first set of permanent magnets of S polarity permanent magnet, the inner side of described vibration damper flange is provided with and comprises at least one pair of N, second set of permanent magnets of S polarity permanent magnet, when state of rest, described first set of permanent magnets is relative between two with the permanent magnet in described second set of permanent magnets, and relative permanent magnet polarity is contrary.
2. crankshaft tortional vibration damper as claimed in claim 1, is characterized in that, leave gap between the magnet of described first set of permanent magnets and described second set of permanent magnets.
3. crankshaft tortional vibration damper as claimed in claim 1, it is characterized in that, at least one limit stoper is provided with between described damper hub and described vibration damper flange, described limit stoper comprises a kidney slot of the inner side being positioned at described vibration damper flange further, and be positioned at inner side one protruding of described damper hub, the stretching into described kidney slot at least partially and can circumferentially move of described projection wherein.
4. crankshaft tortional vibration damper as claimed in claim 3, it is characterized in that, described kidney slot size is circumferentially greater than described projection size circumferentially.
5. crankshaft tortional vibration damper as claimed in claim 4, it is characterized in that, described projection is a rubber parts being connected in the inner side of described damper hub.
6. the crankshaft tortional vibration damper according to any one of claim 1-5, is characterized in that, a crankshaft end flange is connected in the outside of described damper hub.
7. the crankshaft tortional vibration damper according to any one of claim 1-5, is characterized in that, a belt pulley is connected in the outside of described vibration damper flange, can with described vibration damper flange Concentric rotation.
8. crankshaft tortional vibration damper as claimed in claim 7, it is characterized in that, described belt pulley comprises the first belt grooves portion with the first outer diameter.
9. crankshaft tortional vibration damper as claimed in claim 8, it is characterized in that, described belt pulley also comprises the second belt grooves portion with the second outer diameter, and described first outer diameter is less than described second outer diameter.
10. the crankshaft tortional vibration damper according to any one of claim 1-5, it is characterized in that, one clutch shaft bearing, an inner spacing collar, one second bearing are sleeved on described damper hub successively, and described vibration damper flange is enclosed within the outer ring of the outer ring of described clutch shaft bearing, an outer separator and described second bearing regularly.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520596942.0U CN205064694U (en) | 2015-08-07 | 2015-08-07 | Bent axle torsional damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520596942.0U CN205064694U (en) | 2015-08-07 | 2015-08-07 | Bent axle torsional damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205064694U true CN205064694U (en) | 2016-03-02 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520596942.0U Expired - Fee Related CN205064694U (en) | 2015-08-07 | 2015-08-07 | Bent axle torsional damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205064694U (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105649830A (en) * | 2016-03-22 | 2016-06-08 | 郑州航空工业管理学院 | Energy-saving device for preventing idling stop of six-stroke W12 engine |
| CN105649829A (en) * | 2016-03-22 | 2016-06-08 | 郑州航空工业管理学院 | Energy-saving device for preventing idling stop of two-stroke L9 engine |
| CN105736193A (en) * | 2016-03-22 | 2016-07-06 | 郑州航空工业管理学院 | Energy-saving device capable of preventing six-stroke H18 engine from idling stopping |
| CN105822413A (en) * | 2016-03-22 | 2016-08-03 | 郑州航空工业管理学院 | Energy-saving device for preventing two-stroke V8 engine from idling and flaming out |
| CN105822414A (en) * | 2016-03-22 | 2016-08-03 | 郑州航空工业管理学院 | Energy-saving device for preventing two-stroke L3 engine from idling and flaming out |
| CN105822415A (en) * | 2016-03-22 | 2016-08-03 | 郑州航空工业管理学院 | Energy-saving device for preventing six-stroke V9 engine from idling and flaming out |
| CN105840300A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing four-stroke H18 engine from idling stop |
| CN105840299A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing six-stroke VR6 engine from idling stop |
| CN105840301A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing four-stroke V6 engine from idling stop |
| CN105840298A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing two-stroke VR6 engine from idling stop |
-
2015
- 2015-08-07 CN CN201520596942.0U patent/CN205064694U/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105649830A (en) * | 2016-03-22 | 2016-06-08 | 郑州航空工业管理学院 | Energy-saving device for preventing idling stop of six-stroke W12 engine |
| CN105649829A (en) * | 2016-03-22 | 2016-06-08 | 郑州航空工业管理学院 | Energy-saving device for preventing idling stop of two-stroke L9 engine |
| CN105736193A (en) * | 2016-03-22 | 2016-07-06 | 郑州航空工业管理学院 | Energy-saving device capable of preventing six-stroke H18 engine from idling stopping |
| CN105822413A (en) * | 2016-03-22 | 2016-08-03 | 郑州航空工业管理学院 | Energy-saving device for preventing two-stroke V8 engine from idling and flaming out |
| CN105822414A (en) * | 2016-03-22 | 2016-08-03 | 郑州航空工业管理学院 | Energy-saving device for preventing two-stroke L3 engine from idling and flaming out |
| CN105822415A (en) * | 2016-03-22 | 2016-08-03 | 郑州航空工业管理学院 | Energy-saving device for preventing six-stroke V9 engine from idling and flaming out |
| CN105840300A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing four-stroke H18 engine from idling stop |
| CN105840299A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing six-stroke VR6 engine from idling stop |
| CN105840301A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing four-stroke V6 engine from idling stop |
| CN105840298A (en) * | 2016-03-22 | 2016-08-10 | 郑州航空工业管理学院 | Energy-saving device for preventing two-stroke VR6 engine from idling stop |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20170807 Address after: 215000, No. 1, No. 58, Sheng Yin Road, Suzhou Industrial Park, Jiangsu, Suzhou Patentee after: KENDRION ELECTROMAGNETIC TECHNOLOGY (SUZHOU) CO.,LTD. Address before: 210000 Jiangsu city of Nanjing province Qixia economic and Technological Development Zone Run Hua Road No. 14 Patentee before: KENDRION LINNING DRIVE TECH. (NANJING) Co.,Ltd. |
|
| TR01 | Transfer of patent right | ||
| CP03 | Change of name, title or address |
Address after: 215000 No. 2, No. 17 Suhong East Road, Suzhou Industrial Park, Jiangsu Patentee after: KENDRION ELECTROMAGNETIC TECHNOLOGY (CHINA) CO.,LTD. Address before: 215000 No. 1, No. 58, Yin Sheng Road, Sheng Pu zoning, Suzhou Industrial Park, Suzhou, Jiangsu Patentee before: KENDRION ELECTROMAGNETIC TECHNOLOGY (SUZHOU) CO.,LTD. |
|
| CP03 | Change of name, title or address | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160302 Termination date: 20210807 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |