CN205836536U - A kind of double frequency torsional vibration damper for car transmissions - Google Patents
A kind of double frequency torsional vibration damper for car transmissions Download PDFInfo
- Publication number
- CN205836536U CN205836536U CN201620755435.1U CN201620755435U CN205836536U CN 205836536 U CN205836536 U CN 205836536U CN 201620755435 U CN201620755435 U CN 201620755435U CN 205836536 U CN205836536 U CN 205836536U
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- rubber
- mass
- ironware
- spacing
- spacing rubber
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Abstract
The utility model discloses a kind of double frequency torsional vibration damper for car transmissions, including annulus mass block I, annulus mass block II, rubber assembly I, rubber assembly II, spacing rubber V, ironware in annular, outer ironware that cylinder is hood-shaped and for the hood-shaped mounting flange with the cylinder of end part of driving shaft secure fit, described interior ironware is press fit together with mounting flange excircle interference, described mounting flange outer circumferential end face is provided with the positive stop lug boss of ironware axial location in limiting, mounting flange is arranged in outer ironware, the independent fixed and arranged of mass I and mass II side-by-side parallel ground is between mounting flange and outer ironware, and outer ironware is press fit together with mass I interference.This utility model can solve the problem that the problem of two torsional resonance frequencies, and product structure is spacing compact, both can limit the significantly displacement of mass, abnormal sound is there is during collision free, can well improve again the fatigue life of product, easy to process, safe and reliable, it is easy to popularization and application.
Description
Technical field
This utility model belongs to dynamic vibration absorber field, and a kind of double frequency for car transmissions reverses
Vibroshock.
Background technology
Along with the fast development of China's automobile industry, the attention rate of passenger car comfortableness is gradually stepped up by people, and this also will
Requirement to car load NVH performance is more and more higher.And passenger car is under the trend that energy-saving and emission-reduction and body lightening design, preposition
After drive and the drive system of 4-wheel driven car, especially change speed gear box-power transmission shaft-rear bridge portion, easily draws under the excitation of electromotor
Play twisting vibration, cause vehicle body and the resonance of miscellaneous part to cause the noise that thunders of vehicle ride indoor.
How front-engine rear-drive car or 4-wheel driven car, in accelerator, evoke power transmission shaft in the range of rotating speed 1000-2000rpm
Torsional resonance mode, the twisting vibration of power transmission shaft can to the comfortableness of car load and bring the service life of power transmission shaft serious unfavorable
Impact.By setting up torsional vibration damper, the resonant frequency of the natural frequency and power transmission shaft that control vibroshock matches, can be very
The problem solving or reducing Vehicular vibration noise in big degree.
Use more for single-frequency torsional vibration damper, the most only a natural frequency on domestic market, can only solve
The vibration noise of certain frequency range of power transmission shaft.The main driving source of the torsion modes of drive system, from electromotor, starts
The order vibration of machine causes power transmission shaft to there is the resonance of multiple different frequency.In order to meet the vibration damping demand of relatively wide resonance frequency band,
Then needing to install 2 or multiple torsional vibration damper side by side, this just brings certain office at aspects such as installing space, cost and techniques
Sex-limited.
And currently a popular torsional vibration damper majority be not provided with reverse, axially, the most spacing and anti-deprotection of mass
Device, has had a strong impact on the fatigue life of torsional vibration damper and the safety of vehicle drive system, within the shorter use time and
Causing vulcanite to tear under limiting condition, even mass departs from, and destroys drive system and chassis part, jeopardizes driving peace
Entirely.
Utility model content
The purpose of this utility model is to solve the deficiency that above prior art exists, it is provided that a kind of simple in construction, processing
Convenient, the safe and reliable double frequency torsional vibration damper for car transmissions.
For solving above-mentioned technical problem, the technical solution adopted in the utility model is:
A kind of double frequency torsional vibration damper for car transmissions, including annulus mass block I, annulus mass block II, rubber
Outer ironware that in glue assembly I, rubber assembly II, spacing rubber V, annular, ironware, cylinder are hood-shaped and for tight with end part of driving shaft
Gu the hood-shaped mounting flange of cylinder coordinated, described interior ironware is press fit together with mounting flange excircle interference, described company
Acting flange dish outer circumferential end face is provided with the positive stop lug boss of ironware axial location in limiting, and described mounting flange is arranged on outer ferrum
In part, the independent fixed and arranged of described mass I and mass II side-by-side parallel ground is between mounting flange and outer ironware, and outward
Ironware is press fit together with mass I interference, the independent fixed and arranged ferrum outside of rubber assembly I and rubber assembly II side-by-side parallel ground
In part, and lay respectively between interior ironware and mass I, between mass II and positive stop lug boss；Described spacing rubber V and matter
Gauge block II sulfuration is integrated.
Further, described rubber assembly I includes block rubber I, spacing rubber I and spacing rubber II, described block rubber I
Quantity is multiple, is spacedly distributed in the outer circumference surface of interior ironware and mass I inner peripheral surface, mass I by block rubber I with
The sulfuration of interior ironware is integrated；Described spacing rubber I is multiple, and be spacedly distributed the outer circumference surface of ironware in even, and with interior ferrum
Part sulfuration is integrated；Described spacing rubber II is multiple, is spacedly distributed in mass I inner peripheral surface, and vulcanizes with mass I
It is integrated.
Further, described rubber assembly II includes block rubber II, spacing rubber III, spacing rubber IV, described block rubber
II is multiple, is spacedly distributed in the outer circumference surface of positive stop lug boss and mass II inner peripheral surface, and mass II passes through block rubber
II is integrated with positive stop lug boss sulfuration, and described spacing rubber III is multiple, is spacedly distributed in the outer circumference surface of positive stop lug boss, and
It is integrated with positive stop lug boss sulfuration；Described spacing rubber IV is multiple, is spacedly distributed in mass II inner peripheral surface, and and matter
Gauge block II sulfuration is integrated.
Further, the end face of described outer ironware is provided with multiple arcuate socket.Play press-fiting of outer ironware and mass I
Time the positioning action of pressing tool, can control to reverse unbalance dynamic by the quantity and size arranging arcuate socket simultaneously
Amount.
Further, described spacing rubber V is provided with certain gap with the inner peripheral surface of outer ironware.For mass
II plays the effect that radial direction is spacing.
Further, it is provided with certain gap between inside described spacing rubber V and the end face of outer ironware.To quality
Block II plays the effect of axial limiting.
Further, the quantity of described spacing rubber II is the twice of spacing rubber I, and described spacing rubber I is with spacing
Torsional direction and gap radially it is provided with between rubber II.Play and reverse spacing and the most spacing effect.
Further, the quantity of described spacing rubber IV is the twice of spacing rubber III, described spacing rubber III and limit
Torsional direction and gap radially it is provided with between the rubber IV of position.Play and reverse spacing and the most spacing effect.
Further, described mounting flange is provided with can mesopore close-fitting with end part of driving shaft and pilot hole.
The beneficial effects of the utility model are: this utility model can solve the problem that the problem of two torsional resonance frequencies, product
Structure is spacing compact, and spacing place has vulcanite to buffer, and both can limit mass and not have significantly displacement, it is to avoid collision
Shi Fasheng abnormal sound, can well ensure again product life-span will not premature failure, and be provided with anti-loosening protector, improve product
Security reliability, it is easy to by regulation elastomeric material formula and control mass rotary inertia, thus regulate double frequency turn round
Turn the natural frequency of vibroshock.In the process of moving, engine output torque, its torque ripple causes PWTN to vehicle
The twisting vibration of system, when excited frequency is identical with the natural frequency of drive system, causes resonance.For resonance frequency of interest
Rate mate regulation torsional vibration damper natural frequency, the resonance through mass can effectively absorb or decay vibrate energy
Amount, reduces twisting vibration and the noise of drive system, thus improves the riding comfort of car load.
Accompanying drawing explanation
Fig. 1 is that the overall structure front view of this utility model embodiment partly cuts open schematic diagram；
Fig. 2 is the overall structure front view of this utility model embodiment；
Fig. 3 is A-A cross-sectional view in Fig. 2；
Fig. 4 is the overall structure signal explosive view of this utility model embodiment；
In figure, label is as follows with title:
1-mounting flange；11-positive stop lug boss；12-mesopore；13-pilot hole；
Ironware in 2-；
3-rubber assembly I；31-block rubber I；The spacing rubber of 32-I；The spacing rubber of 33-II；
4-mass I；
5-rubber assembly II；51-block rubber II；The spacing rubber of 52-III；The spacing rubber of 53-IV；
6-mass II；
The spacing rubber of 7-V；
The outer ironware of 8-；81-arcuate socket.
Detailed description of the invention
For ease of it will be appreciated by those skilled in the art that below in conjunction with the accompanying drawings and this utility model is made further in detail by embodiment
Describe in detail bright.
As shown in Figures 1 to 4, a kind of double frequency torsional vibration damper for car transmissions, including annulus mass block I 4,
The outer ironware that the interior ironware 2 of annulus mass block II 6, rubber assembly I 3, rubber assembly II 5, spacing rubber V 7, annular, cylinder are hood-shaped
8 and for the hood-shaped mounting flange 1 with the cylinder of end part of driving shaft secure fit, described interior ironware 2 and mounting flange 1 cylindrical
Week interference is press fit together, and described mounting flange 1 outer circumferential end face is provided with the positive stop lug boss of ironware 2 axial location in limiting
11, its objective is to play axial limiting effect when interior ironware 2 is pressed into mounting flange 1.Described mounting flange 1 is arranged on outer ferrum
In part 8, the independent fixed and arranged of described mass I 4 and mass II 6 side-by-side parallel ground mounting flange 1 and outer ironware 8 it
Between, and outer ironware 8 is press fit together with mass I 4 interference, rubber assembly I 3 and rubber assembly II 5 side-by-side parallel ground are independent solid
Surely it is arranged in outer ironware 8, and lays respectively between interior ironware 2 and mass I 4, between mass II 6 and positive stop lug boss 11；
Described spacing rubber V 7 is integrated with mass II 6 sulfuration.
Described rubber assembly I 3 includes block rubber I 31, spacing rubber I 32 and spacing rubber II 33, described rubber assembly
II 5 include block rubber II 51, spacing rubber III 52, spacing rubber IV 53,
Described block rubber I 31 and block rubber II 51 side-by-side parallel, independent layout；Block rubber I 31 quantity is 4, between waiting
The outer circumference surface of ironware 2 and mass I 4 inner peripheral surface in the company of being distributed in, and be integrated with interior ironware 2, mass I 4 sulfuration；
Described block rubber II 51 is also 4, is spacedly distributed in the outer circumference surface of mounting flange positive stop lug boss 11 and mass II 6
Inner peripheral surface, and be integrated with positive stop lug boss 11, mass II 6 sulfuration.
Spacing rubber I 32 has 4, and be spacedly distributed the outer circumference surface of ironware 2 within connecting, and is one with the sulfuration of interior ironware 2
Body；Spacing rubber II 33 has 8, is spacedly distributed in mass I 4 inner peripheral surface, and is integrated with mass I 4 sulfuration；Spacing
There is gap axially and radially between rubber I 32 and spacing rubber II 33, controlled axially and footpath by the size setting gap
To spacing, protect block rubber I 31 be unlikely to large angle torsion or be torn under power transmission shaft limit twisting conditions simultaneously, from
And improve the fatigue life of rubber assembly I 3.
Spacing rubber III 52 has 4, is spacedly distributed in the outer circumference surface of mounting flange positive stop lug boss 11, and with spacing
Boss 11 sulfuration is integrated；Spacing rubber IV 53 has 8, is spacedly distributed in mass II 6 inner peripheral surface, and with mass II
6 sulfurations are integrated；Gap axially and radially is had, by setting the big of gap between spacing rubber III 52 and spacing rubber IV 53
Little control axially and radially spacing, protect block rubber II 51 to be unlikely to big angle under power transmission shaft limit twisting conditions simultaneously
Degree reverses or is torn, thus improves the fatigue life of rubber assembly II 5.
Spacing rubber V 7 and mass II 6 sulfuration one, the effect of spacing rubber V 7 is: under some driving operating mode,
Mass II 6 realizing soft contact when colliding with mass I 4, outer ironware 8, limit simultaneously mass II 6 axially and
Radial displacement, it is to avoid ironware produces noise with ironware collision and improves the security reliability of product.
Interior ironware 2 is press fit together with mounting flange 1 interference, and is limited by the inner face axial limiting of positive stop lug boss 11
The press-in displacement of ironware 2 in system, it is ensured that mass I 4 and rubber assembly I 3, mass II 6 and rubber assembly II 5 are separate,
Non-interference；
The end face of described outer ironware 8 is provided with 6 arcuate sockets, plays location and controls the effect of unbalancing value, outer ferrum
Part 8 is press fit together with mass I 4 interference；Outer ironware 8 plays the effect of protective cover simultaneously, even if block rubber I 31 fracture also will not
Abjection；Same, even if block rubber II 51 ruptures, also it is not result in that mass II 6 is deviate from.
Described spacing rubber V 7 is provided with certain gap with the inner peripheral surface of outer ironware 8.For II radial direction of mass
Spacing effect.
It is provided with certain gap between inside described spacing rubber V 7 and the end face of outer ironware 8.To II axle of mass
To spacing effect.
The quantity of described spacing rubber II 33 is the twice of spacing rubber I 32, described spacing rubber I and spacing rubber II
Between be provided with torsional direction and gap radially.Play and reverse spacing and the most spacing effect.
The quantity of described spacing rubber IV 53 is the twice of spacing rubber III 52, described spacing rubber III 52 and spacing rubber
Torsional direction and gap radially it is provided with between glue IV 53.Play and reverse spacing and the most spacing effect.
Described mounting flange 1 is provided with can mesopore 12 close-fitting with end part of driving shaft and pilot hole 13.
The present embodiment regulates rubber torsional rigidity and damping by the formula of elastomeric material, and combines regulation mass
Rotary inertia can realize the optimal control of torsional vibration damper natural frequency, thus mates drive system torsion to be solved altogether
Vibration frequency, the problem solving two torsional resonance frequencies, product structure is spacing compact, and spacing place has vulcanite to buffer,
Both the significantly displacement of mass can have been limited, it is to avoid abnormal sound occurs during collision, can well improve again the fatigue life of product, and
It is provided with anti-loosening protector, improves the security reliability of product.Product structure is simple, easy to process, safe and reliable, it is easy to push away
Wide application.
The foregoing is only preferred embodiment of the present utility model, not in order to limit this utility model, all at this
Any amendment, equivalent or the improvement etc. made within the spirit of utility model and principle, should be included in this utility model
Protection domain within.
Claims (9)
1. the double frequency torsional vibration damper for car transmissions, it is characterised in that: include annulus mass block I (4), annular
The interior ironware (2) of mass II (6), rubber assembly I (3), rubber assembly II (5), spacing rubber V (7), annular, cylinder are hood-shaped
Outer ironware (8) and for the hood-shaped mounting flange (1) with the cylinder of end part of driving shaft secure fit, described interior ironware (2) with even
Acting flange dish (1) excircle interference is press fit together, and described mounting flange (1) outer circumferential end face is provided with ironware in restriction
(2) positive stop lug boss (11) of axial location, in described mounting flange (1) is arranged on outer ironware (8), described mass I (4) and
The independent fixed and arranged in mass II (6) side-by-side parallel ground between mounting flange (1) and outer ironware (8), and outer ironware (8) and
Mass I (4) interference is press fit together, and the independent fixed and arranged of rubber assembly I (3) and rubber assembly II (5) side-by-side parallel ground exists
In outer ironware (8), and lay respectively between interior ironware (2) and mass I (4), mass II (6) and positive stop lug boss (11) it
Between；Described spacing rubber V (7) is integrated with mass II (6) sulfuration.
Double frequency torsional vibration damper the most according to claim 1, it is characterised in that: described rubber assembly I (3) includes rubber
Block I (31), spacing rubber I (32) and spacing rubber II (33), described block rubber I (31) quantity is multiple, be spacedly distributed in
The outer circumference surface of interior ironware (2) and mass I (4) inner peripheral surface, mass I (4) is by block rubber I (31) and interior ironware (2)
Sulfuration is integrated；Described spacing rubber I (32) is multiple, and be spacedly distributed the outer circumference surface of ironware (2) in even, and with interior ferrum
Part (2) sulfuration is integrated；Described spacing rubber II (33) is multiple, is spacedly distributed in mass I (4) inner peripheral surface, and with
Mass I (4) sulfuration is integrated.
Double frequency torsional vibration damper the most according to claim 1, it is characterised in that: described rubber assembly II (5) includes rubber
Block II (51), spacing rubber III (52), spacing rubber IV (53), described block rubber II (51) is multiple, is spacedly distributed in limit
The outer circumference surface of position boss (11) and mass II (6) inner peripheral surface, mass II (6) is by block rubber II (51) and limit convex
Platform (11) sulfuration is integrated, and described spacing rubber III (52) is multiple, is spacedly distributed in the outer circumference surface of positive stop lug boss (11),
And be integrated with positive stop lug boss (11) sulfuration；Described spacing rubber IV (53) is multiple, is spacedly distributed in mass II (6)
Periphery, and be integrated with mass II (6) sulfuration.
Double frequency torsional vibration damper the most according to claim 1, it is characterised in that: the end face of described outer ironware 8 is provided with
Multiple arcuate sockets (81).
Double frequency torsional vibration damper the most according to claim 1, it is characterised in that: described spacing rubber V (7) and outer ferrum
The inner peripheral surface of part (8) is provided with certain gap.
Double frequency torsional vibration damper the most according to claim 1, it is characterised in that: described spacing rubber V (7) and outer ferrum
It is provided with certain gap between inside the end face of part (8).
Double frequency torsional vibration damper the most according to claim 2, it is characterised in that: the quantity of described spacing rubber II (33)
It is the twice of spacing rubber I (32), between described spacing rubber I (32) and spacing rubber II (33), is provided with torsional direction and radial direction
Gap.
Double frequency torsional vibration damper the most according to claim 3, it is characterised in that: the quantity of described spacing rubber IV 53 is
The twice of spacing rubber III (52), is provided with torsional direction and radial direction between described spacing rubber III (52) and spacing rubber IV (53)
Gap.
Double frequency torsional vibration damper the most according to claim 1, it is characterised in that: described mounting flange (1) is provided with
Can mesopore close-fitting with end part of driving shaft (12) and pilot hole (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620755435.1U CN205836536U (en) | 2016-07-15 | 2016-07-15 | A kind of double frequency torsional vibration damper for car transmissions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620755435.1U CN205836536U (en) | 2016-07-15 | 2016-07-15 | A kind of double frequency torsional vibration damper for car transmissions |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205836536U true CN205836536U (en) | 2016-12-28 |
Family
ID=57619846
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620755435.1U Expired - Fee Related CN205836536U (en) | 2016-07-15 | 2016-07-15 | A kind of double frequency torsional vibration damper for car transmissions |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205836536U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109210143A (en) * | 2018-11-07 | 2019-01-15 | 安徽中鼎减震橡胶技术有限公司 | A kind of transmission shaft absorber block |
| CN111288148A (en) * | 2020-02-12 | 2020-06-16 | 常州工学院 | High-damping double-frequency dynamic vibration reduction gear transmission device |
| CN112032249A (en) * | 2020-08-05 | 2020-12-04 | 华东交通大学 | Novel automobile transmission shaft rubber torsional damper |
-
2016
- 2016-07-15 CN CN201620755435.1U patent/CN205836536U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109210143A (en) * | 2018-11-07 | 2019-01-15 | 安徽中鼎减震橡胶技术有限公司 | A kind of transmission shaft absorber block |
| CN109210143B (en) * | 2018-11-07 | 2023-10-20 | 安徽中鼎减震橡胶技术有限公司 | Vibration absorbing block of transmission shaft |
| CN111288148A (en) * | 2020-02-12 | 2020-06-16 | 常州工学院 | High-damping double-frequency dynamic vibration reduction gear transmission device |
| CN112032249A (en) * | 2020-08-05 | 2020-12-04 | 华东交通大学 | Novel automobile transmission shaft rubber torsional damper |
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Legal Events
| 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 | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20161228 Termination date: 20190715 |