CN220488195U - Vibration damper with damper comprising a channel - Google Patents
Vibration damper with damper comprising a channel Download PDFInfo
- Publication number
- CN220488195U CN220488195U CN202190000856.2U CN202190000856U CN220488195U CN 220488195 U CN220488195 U CN 220488195U CN 202190000856 U CN202190000856 U CN 202190000856U CN 220488195 U CN220488195 U CN 220488195U
- Authority
- CN
- China
- Prior art keywords
- damper
- stopper
- channel
- vibration damper
- lateral surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000003247 decreasing effect Effects 0.000 claims abstract description 3
- 230000005540 biological transmission Effects 0.000 claims description 4
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 238000013016 damping Methods 0.000 description 7
- 230000033001 locomotion Effects 0.000 description 4
- 229920001971 elastomer Polymers 0.000 description 3
- 239000000806 elastomer Substances 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/127—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs using plastics springs combined with other types of springs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The utility model relates to a vibration damper (10) for transmitting a drive applied by an engine to a gearbox in a vehicle, and comprising at least one spring (14) positioned within at least one spring housing (12) provided on a drive plate (11) and at least one stopper (20) positioned in said spring (14). As an improvement, the stopper (20) is provided with a cylindrical shape with a diameter decreasing towards the end and at least one channel (21) is provided on the stopper (20) extending along the diameter of the stopper.
Description
Technical Field
The present utility model relates to a vibration damper for transmitting a drive applied by an engine to a transmission in a vehicle.
Background
The subject vibration damper is used to transfer motion, particularly that imparted by an engine on a torque limiter, to a transfer unit in a vehicle. Accordingly, the motion imparted by the motor is transferred from the drive plate to the retainer plate. Due to the brake lining connected to the retainer plate, when the torque exceeds a predetermined value, the brake lining wears and prevents excessive torque from being transmitted to the transmission unit. The transfer of motion from the drive plate to the holder plate is achieved by means of springs located between the drive plate and the holder plate. Thus, first, the drive plate compresses the spring and prevents movement from being transferred to the retainer plate in a rough manner.
The stopper disclosed in the application numbered US 5690553A has an elastomeric portion located between two end portions. The end portion and the elastomeric portion are connected to each other by means of rivets.
When the elastomer part used in the embodiment is forced to be compressed, the length of the elastomer part is shortened. When the applied force is removed, the elastomeric portion cannot return to its original length. In other words, when the elastomer part is subjected to a force, the plastic part changes shape and its length is shortened. This results in a deviation of the tolerance of the vibration damper.
As a result, due to all of the above problems, improvements are required in the related art.
Disclosure of Invention
The present utility model relates to a vibration damper for eliminating the above-mentioned drawbacks and bringing new advantages to the related art.
It is an object of the present utility model to provide a vibration damper with a damper in which the length loss associated with plastic shape changes during operation is reduced.
To achieve all the above objects and those which will be derived from the following detailed description, the present utility model is a vibration damper for transmitting a drive applied by an engine to a gearbox in a vehicle, and comprising at least one spring positioned within at least one spring housing provided on a drive plate, and at least one stopper positioned in said spring. Accordingly, at least one channel is provided on the stopper extending along at least a portion of the outer diameter of the stopper. Thus, the stress applied to the stopper is distributed in a balanced manner, and plastic deformation occurring in the stopper after compression is reduced.
In a preferred embodiment of the utility model, at least one channel is provided on the stopper extending along the entire outer diameter of the stopper. Thus, the stress applied to the stopper is more effectively distributed in a balanced manner, and plastic deformation occurring in the stopper after compression is reduced.
In a preferred embodiment of the utility model, the two channels are arranged in a symmetrical manner with respect to the middle of the stopper.
In a preferred embodiment of the utility model, the total channel width present on the stopper when the stopper is not compressed is less than the length variation that occurs in the stopper when the stopper is compressed.
In a preferred embodiment of the utility model, the total channel width present on the stopper when the stopper is not compressed is greater than or equal to the length variation that occurs in the stopper when the stopper is compressed.
In a preferred embodiment of the utility model, the stopper is provided in a cylindrical shape having a lateral surface diameter decreasing towards the end.
In a preferred embodiment of the utility model, the lateral surface of the stopper is provided with a rounded profile.
In a preferred embodiment of the utility model, the lateral surface diameter of the lateral surface of the stopper is equal to or greater than twice the length of the stopper.
In a preferred embodiment of the utility model, the lateral surface diameter of the lateral surface of the stopper is equal to or less than three times the length of the stopper.
In a preferred embodiment of the utility model, the sum of the distances from the channel bottom defining the deepest part of each channel to the center of the stopper when the stopper is not compressed is greater than or equal to the length change that occurs in the stopper when the stopper is compressed.
Drawings
Fig. 1 shows a representative detailed view of a vibration damper of the present disclosure.
Fig. 2 illustrates a representative isometric view of a damper of the vibration damper of the present disclosure.
Fig. 3 shows a representative isometric cross-sectional view of a damper of a vibration damper of the present disclosure.
Fig. 4a, 4b, 4c show representative isometric views of an exemplary embodiment of a damper of a vibration damper of the present disclosure.
Fig. 5 shows a stress distribution of an exemplary embodiment of a damper of a vibration damper used in the prior art.
Fig. 6 illustrates stress distribution of an exemplary embodiment of a damper of a vibration damper of the present disclosure.
Fig. 7 shows the angle-torque variation pattern for the following cases: wherein the total channel width across the damper of the vibration damper of the present disclosure is greater than the amount of compression that occurs in the damper.
Fig. 8 shows the angle-torque variation pattern for the following cases: wherein the total channel width across the damper of the vibration damper of the present disclosure is less than the amount of compression that occurs in the damper.
In fig. 9, a graph of plastic shape changes occurring in the range of 2l < r <3l in an exemplary embodiment of a damper of a vibration damper of the present disclosure is shown.
In fig. 10, a graph of plastic shape changes occurring in a damper according to the amount of difference between the damper length and the channel bottom radius in an exemplary embodiment of the damper of the vibration damper of the present disclosure is shown.
Detailed Description
In this detailed description, the subject vibration damper (10) is explained with reference to examples only for the purpose of making the subject matter more understandable, without any limiting effect.
Referring to fig. 1, the subject vibration damper (10) is used to transfer drive applied by an engine to a transmission. In an exemplary embodiment of the utility model, the vibration damper (10) has a drive plate (11). At least one spring housing (12) is arranged on the drive plate (11). At least one spring (14) is arranged in the spring housing (12). At both ends of the spring (14) at least one spring holder (13) is provided for providing a fixation of the spring (14). In a possible embodiment of the utility model, two springs (14) may be provided, which telescopically engage each other. The spring holder (13) may be made of a plastic-based material or a metal-based material. At least one stopper (20) is provided in the inner gap of the spring (14). After the spring (14) is compressed by a predetermined amount, the damper (20) is compressed and provides damping.
As can be seen in fig. 2 and 3, the stopper (20) is provided in a cylindrical shape. Furthermore, the stopper (20) is provided such that its outer diameter narrows toward both ends thereof. In other words, the lateral surface (23) of the stopper (20) is embodied with a lateral surface diameter (R). The stopper (20) has a stopper length (L). The stopper length (L) is the distance in the axial direction between the two axial ends of the stopper (20). A stopper (20) extends integrally between the two axial ends. A center axis (X) is provided at the center of a stopper (20) provided in a cylindrical shape. The central axis (X) extends in an axial direction.
The stopper (20) is provided with at least one passage (21). The channel (21) extends along at least a portion of the perimeter of the stopper (20) on a lateral surface (23) of the stopper (20). In other words, the channel (21) is made of a series of holes. In a possible embodiment of the utility model not all holes are in communication with each other.
In a possible embodiment of the utility model, all the holes of the channel (21) are in communication with each other. In other words, said channel (21) extends along the entire perimeter of the stopper (20) on the lateral surface (23) of the stopper (20).
The channel (21) is embodied with a channel width (t). The channel width (t) extends in the axial direction. Further, a distance from a channel bottom (22) of the channel (t) to the central axis (X) is defined as a channel bottom radius (d). Referring to fig. 4a, one channel (21) may be provided in the middle of the stopper (20), referring to fig. 4b, two channels may be symmetrically provided with respect to the middle of the stopper (20), or referring to fig. 4c, one channel may be provided in the middle of the stopper (20) and one channel may be provided at each side of the middle of the stopper (20). In alternative embodiments, the number of channels (21) may be greater than three.
In a possible embodiment of the utility model, all the holes of the rib communicate with each other.
When the stopper (20) is compressed such that its length decreases during operation, the channel (21) provides that the stresses present on the stopper (20) are distributed in a more balanced manner. In other words, in the related art, when the stopper (20) is compressed, loads accumulate at both end portions of the stopper (20) and cause plastic deformation at these portions (fig. 5—related art). In the stopper (20) having the passage (21), since the outer diameter and the lateral surface diameter (R) of the portion where the passage (21) is located are reduced when the stopper (20) is compressed, stress accumulation around the passage (21) is also observed. Therefore, in the portion where no shape change occurs in the prior art, the shape change is now observed, and plastic deformation occurring in the stopper (20) is reduced (fig. 6).
In a possible embodiment of the utility model, the total channel width (t) over the stopper (20) is set to be larger than the amount of compression occurring in the stopper (20). Thus, during compression, the two side walls of the channel (21) are prevented from contacting each other, and therefore, in the vibration damper (10), damping depending on the characteristics of the spring (14) occurs first, and damping depending on the characteristics of the stopper (20) occurs later (fig. 7).
In another possible embodiment of the utility model, the total channel width (t) over the stopper (20) is set smaller than the amount of compression occurring in the stopper (20). Thus, during compression, the two side walls of the channel (21) are in contact with each other. Therefore, in the vibration damper (10), first, damping depending on the characteristics of the spring (14) occurs, then damping depending on the characteristics of the stopper (20) occurs, and then, when the side walls abut against each other, the stopper (20) forms different damping characteristics (fig. 8).
Thus, the total channel width (t) over the damper (20) is changed, and the vibration damper (10) can realize damping with different characteristics.
In a possible embodiment of the utility model, the lateral surface diameter (R) of the lateral surface is set to be less than or equal to three times the stopper length (L). This is independent of the position of the lateral surface diameter (R). In other words, the maximum lateral surface diameter (R) of the stopper (20) is less than or equal to three times the stopper length (L).
In another possible embodiment of the utility model, the lateral surface diameter (R) of the lateral surface is set to be less than or equal to twice the stopper length (L). This is independent of the position of the lateral surface diameter (R). In other words, the maximum lateral surface diameter (R) of the stopper (20) is less than or equal to twice the stopper length (L).
In the graph given in fig. 9, the vertical axis describes the amount of plastic deformation that occurs in the stopper (20), and the horizontal axis describes the difference (R-2L) between the lateral surface diameter (R) and twice the stopper length (L). When r=2l, in other words, when R-2l=0, and when r=3l, the amount of plastic deformation is kept at an acceptable level, and in the range of 2L < R <3L, the deformation amount is reduced to a lower value. When R >2L or R >3L, the deformation amount increases to a larger level.
In a possible embodiment of the utility model, the sum of the distances from the channel bottom (22) defining the deepest part of each channel (21) to the centre of the stopper (20) is greater than or equal to the length variation occurring in the stopper (20) when the stopper (20) is compressed. In other words, the sum of the channel bottom radii (d) of all channels (21) provided on the stopper (20) is larger than the length variation occurring at the stopper (20). This is independent of the position of the channel (21) in the stopper (20). In other words, the channel bottom radius (d) of the channel (21) provided on the thinnest portion of the stopper (20) is greater than the length variation that occurs at the stopper (20). In the graph given in fig. 10, the horizontal axis shows the length change, and the vertical axis shows the amount of plastic deformation occurring in the stopper. Accordingly, in experiments performed so that the length variation is 2mm, it has been determined that the plastic deformation amount is at a low level when the sum of the channel bottom radii (d) is greater than 2 mm. In other words, when the sum of the radii of the channel bottoms is less than 2mm, the amount of plastic deformation increases.
The scope of the utility model is set forth in the appended claims and is not limited to the illustrative disclosure set forth in the detailed description above. As it will be apparent to those skilled in the relevant art(s) in light of the foregoing disclosure that similar embodiments can be made without departing from the general principles of the utility model.
Reference numerals
10. Vibration damper
11. Driving plate
12. Spring shell
13. Spring retainer
14. Spring
20. Barrier device
21. Channel
22. Channel bottom
23. Lateral surface
t channel width
Diameter of R lateral surface
L-stop length
X central axis
d radius of channel bottom
Claims (10)
1. A vibration damper (10) for transmitting a drive applied by an engine to a transmission in a vehicle, the vibration damper comprising:
at least one spring (14) located within at least one spring housing (12) provided on the drive plate (11), and
at least one stopper (20) located in the spring (14), characterized in that,
the vibration damper further comprises at least one channel (21) extending over the damper (20) along at least a portion of the outer diameter of the damper.
2. The vibration damper (10) according to claim 1, characterized in that the at least one channel (21) extends over the damper (20) along the entire outer diameter of the damper.
3. Vibration damper (10) according to claim 1 or 2, comprising two channels (21) arranged in a symmetrical manner with respect to the middle of the damper (20).
4. The vibration damper (10) according to claim 1, characterized in that the total channel width (t) present on the damper (20) when the damper (20) is not compressed is smaller than the length variation occurring in the damper (20) when the damper (20) is compressed.
5. The vibration damper (10) according to claim 1, characterized in that the total channel width (t) present on the damper (20) when the damper (20) is not compressed is greater than or equal to the length variation occurring in the damper (20) when the damper (20) is compressed.
6. Vibration damper (10) according to claim 1, characterized in that the damper (20) is provided as a cylindrical profile with a lateral surface diameter (R) decreasing towards the end.
7. The vibration damper (10) according to claim 6, characterized in that the lateral surface of the stopper (20) is provided with a circular profile.
8. The vibration damper (10) according to claim 7, characterized in that the lateral surface diameter (R) of the damper (20) is equal to or greater than twice the damper length (L).
9. Vibration damper (10) according to claim 7 or 8, characterized in that the lateral surface diameter (R) of the lateral surface of the stopper (20) is equal to or smaller than three times the stopper length (L).
10. The vibration damper (10) according to claim 1, characterized in that the sum of the distances from the channel bottom (22) defining the deepest part of each channel (21) to the center of the damper (20) when the damper (20) is not compressed is greater than or equal to the length change occurring in the damper (20) when the damper (20) is compressed.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TR2020/14775 | 2020-09-17 | ||
| TR2020/14775A TR202014775A2 (en) | 2020-09-17 | 2020-09-17 | A VIBRATION DAMPER WITH A STOPPER WITH DUCT |
| PCT/EP2021/075550 WO2022058467A1 (en) | 2020-09-17 | 2021-09-16 | A vibration dampener having a stopper comprising a channel |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220488195U true CN220488195U (en) | 2024-02-13 |
Family
ID=77951683
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202190000856.2U Active CN220488195U (en) | 2020-09-17 | 2021-09-16 | Vibration damper with damper comprising a channel |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN220488195U (en) |
| TR (1) | TR202014775A2 (en) |
| WO (1) | WO2022058467A1 (en) |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2727725C2 (en) * | 1977-06-21 | 1985-06-05 | Fichtel & Sachs Ag, 8720 Schweinfurt | Clutch disc with torsion damper |
| JPH07293578A (en) | 1994-04-25 | 1995-11-07 | Daikin Mfg Co Ltd | Torsion damper for damper disc |
| JP4455858B2 (en) * | 2003-09-30 | 2010-04-21 | アイシン精機株式会社 | Torsion damper |
| WO2012137234A1 (en) * | 2011-04-01 | 2012-10-11 | トヨタ自動車株式会社 | Torsional vibration damping device |
-
2020
- 2020-09-17 TR TR2020/14775A patent/TR202014775A2/en unknown
-
2021
- 2021-09-16 WO PCT/EP2021/075550 patent/WO2022058467A1/en active Application Filing
- 2021-09-16 CN CN202190000856.2U patent/CN220488195U/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| WO2022058467A1 (en) | 2022-03-24 |
| TR202014775A2 (en) | 2022-03-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |