CN104074553B - A kind of turbosupercharger damper - Google Patents
A kind of turbosupercharger damper Download PDFInfo
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- CN104074553B CN104074553B CN201410345024.0A CN201410345024A CN104074553B CN 104074553 B CN104074553 B CN 104074553B CN 201410345024 A CN201410345024 A CN 201410345024A CN 104074553 B CN104074553 B CN 104074553B
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- end surface
- damper
- damping
- damping fin
- fin
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Abstract
The invention discloses the damper in a kind of turbocharger rotor system, axial impact and radial impact can be resisted simultaneously, and damping ratio is adjustable, different supercharger rotor system can be met to the requirement of damping ratio size, to reduce the vibration of supercharger rotor system, improve the Applicable scope of pressurized machine, belong to field of turbochargers.Damper comprises the damping fin of one group of special shape, the quantity of damping fin, can adjust according to the requirement of supercharger rotor system damping rate.
Description
Technical field
The present invention proposes the damper in a kind of turbocharger rotor system, for reducing the vibration of supercharger rotor system, improving the anti-axial impact of rotor-support-foundation system and radial impact ability, belonging to field of turbochargers.
Background technique
Turbosupercharger, day by day towards precise treatment future development, in order to adapt to the change of engine operating condition, reducing the vibration of supercharger rotor system, improving the shock proof ability of rotor-support-foundation system, also more and more higher to the requirement of damper in rotor-support-foundation system.
Adopt the rotor-support-foundation system of floating bearing mainly to impact by the oil film opposing of floating bearing, adopt the rotor-support-foundation system of ball bearing then to need special damper opposing to impact.General damper is divided into axial damper and radial damper two kinds, and rotor-support-foundation system will resist axial impact needs axial damper, and the impact of opposing radial direction needs radial damper.
Summary of the invention
The present invention proposes a kind of turbosupercharger damper, can resist axial impact and radial impact, and damping ratio is adjustable simultaneously, different supercharger rotor system can be met to the requirement of damping ratio size, to reduce the vibration of supercharger rotor system, improve the Applicable scope of pressurized machine.
A kind of turbosupercharger damper, as shown in Figure 1, comprise the damping fin of one group of special shape, single damping fin is made up of upper-end surface, inclined-plane and lower end surface, upper-end surface is parallel with lower end surface, the outside diameter of upper-end surface is less than the interior circular diameter of lower end surface, and the cylindrical of upper-end surface is connected with the inner circle of lower end surface by inclined-plane.Damper is arranged between bearing and bearing support, and two adjacent damping fins rely on the phase mutual friction on contact inclined-plane to produce frictional damping.
Damper is arranged between the ball bearing of turbosupercharger and bearing support, and carries out pretension by the nut of supercharger rotor system.
Further, single damping fin is made up of spring steel, and upper-end surface and lower end surface, through machining, ensure respective planeness and the parallelism of upper and lower end face.
Further, damping fin thickness is 0.3 ~ 0.8mm, preferred 0.5mm; The distance of damping fin upper-end surface and lower end surface is 0.8 ~ 1.5mm, preferred 1mm.
Further, damping fin inclined-plane and lower end surface angle are 150 °, and in upper-end surface outside diameter and lower end surface, the difference of circular diameter is 2mm; Damping fin upper-end surface width and lower end surface width ratio are 1:3.
Further, in damper, the quantity of damping fin is 5 ~ 15, preferably 8.
As shown in Figure 2, in damper free state, the contact of incline plane of adjacent two panels damper, upper and lower end face does not all contact.
When rotor-support-foundation system is subject to axial impact, the inclined-plane of adjacent damping fin produces relative displacement, and the inclined-plane of damping fin deforms simultaneously, two end in contact of adjacent damping fin, the frictional damping opposing axial impact that damping fin bevel friction produces.
When rotor-support-foundation system is subject to radial impact, the inclined-plane of adjacent damping fin produces relative displacement, and the inclined-plane of damping fin deforms simultaneously, the one or both ends contact of adjacent damping fin, the frictional damping opposing radial impact that damping fin bevel friction produces.
By adjusting the quantity of damping fin in the difference of circular diameter in the distance of single damping fin upper-end surface and lower end surface, upper-end surface outside diameter and lower end surface, damper, can the size of damping adjusting device damping ratio, with satisfied different supercharger rotor system to the requirement of damping ratio size.
In damper damping fin number, by the distance between ball bearing and bearing support, system damping rate size and ball bearing play require comprehensively determine.
The invention has the advantages that:
1, this damper can resist axial impact and the radial impact of rotor-support-foundation system simultaneously;
2, the damping ratio of damper is adjustable, can meet different supercharger rotor system to the requirement of damping ratio size;
3, structure is simple, is convenient to processing.
Accompanying drawing explanation
Fig. 1 is front view and the sectional view of damper structure of the present invention;
Fig. 2 is the amplification view of damper structure of the present invention;
Fig. 3 is the erection drawing in damper of the present invention application;
In figure:
1-damping fin 1 2-damping fin 2 3-damping fin 3 4-damping fin 4
5-damping fin 5 6-bearing support 7-damper 8-ball bearing
9-rotating shaft 10-sleeve
Embodiment
The present invention proposes a kind of turbosupercharger damper, can resist axial impact and radial impact, and damping ratio is adjustable simultaneously, different supercharger rotor system can be met to the requirement of damping ratio size, to reduce the vibration of supercharger rotor system, improve the Applicable scope of pressurized machine.
A kind of turbosupercharger damper, as shown in Figure 1, comprises the damping fin of one group of special shape, the quantity of one group of damping fin, can adjust according to the requirement of supercharger rotor system damping rate.
Single damping fin is made up of spring steel, and as shown in Figure 3, one group of damping fin is arranged between 8 ball bearings and 6 bearing supports, and carries out pretension by the nut of supercharger rotor system.Two adjacent damping fins rely on the phase mutual friction on contact inclined-plane to produce frictional damping.When rotor-support-foundation system is subject to axial impact, the inclined-plane of adjacent damping fin produces relative displacement, and damping fin inclined-plane deforms simultaneously, two end in contact of adjacent damping fin, the frictional damping opposing axial impact that damping fin bevel friction produces.When rotor-support-foundation system is subject to radial impact, the inclined-plane of adjacent damping fin produces relative displacement, and damping fin inclined-plane deforms simultaneously, the one or both ends contact of adjacent damping fin, the frictional damping opposing radial impact that damping fin bevel friction produces.
By adjusting the quantity of damping fin in the difference of circular diameter in the distance of single damping fin upper-end surface and lower end surface, upper-end surface outside diameter and lower end surface, damper, can the size of damping adjusting device damping ratio, with satisfied different supercharger rotor system to the requirement of damping ratio size.
In damper damping fin number, by the distance between ball bearing and bearing support, system damping rate size and ball bearing play require comprehensively determine.
Claims (14)
1. a turbosupercharger damper, is characterized in that: damper is made up of one group of damping fin, and each damping fin specification is consistent; Described damping fin is made up of upper-end surface, inclined-plane and lower end surface, and upper-end surface is parallel with lower end surface, and the outside diameter of upper-end surface is less than the interior circular diameter of lower end surface, and the cylindrical of upper-end surface is connected with the inner circle of lower end surface by inclined-plane; Damping fin inclined-plane and lower end surface angle are 150 °, and in upper-end surface outside diameter and lower end surface, the difference of circular diameter is 2mm; Damping fin upper-end surface width and lower end surface width ratio are 1:3.
2. damper as claimed in claim 1, is characterized in that: described damping fin is made up of spring steel.
3. damper as claimed in claim 1 or 2, is characterized in that: damping fin thickness is 0.3 ~ 0.8mm; The distance of damping fin upper-end surface and lower end surface is 0.8 ~ 1.5mm.
4. damper as claimed in claim 3, is characterized in that: damping fin thickness is 0.5mm; The distance of damping fin upper-end surface and lower end surface is 1mm.
5. the damper as described in claim 1 or 2 or 4, is characterized in that: described damper is arranged between the ball bearing of turbosupercharger and bearing support, and carries out pretension by the nut of supercharger rotor system.
6. damper as claimed in claim 3, is characterized in that: described damper is arranged between the ball bearing of turbosupercharger and bearing support, and carries out pretension by the nut of supercharger rotor system.
7. the damper as described in claim 1 or 2 or 4 or 6, it is characterized in that: in damper, the quantity of damping fin is required comprehensively to determine by the distance between ball bearing and bearing support, system damping rate size and ball bearing play, and described quantity is 5 ~ 15.
8. damper as claimed in claim 3, is characterized in that: in damper, the quantity of damping fin is required comprehensively to determine by the distance between ball bearing and bearing support, system damping rate size and ball bearing play, and described quantity is 5 ~ 15.
9. damper as claimed in claim 5, is characterized in that: in damper, the quantity of damping fin is required comprehensively to determine by the distance between ball bearing and bearing support, system damping rate size and ball bearing play, and described quantity is 5 ~ 15.
10. damper as claimed in claim 7, is characterized in that: in damper, the quantity of damping fin is 8.
11. dampers as claimed in claim 8 or 9, is characterized in that: in damper, the quantity of damping fin is 8.
12. dampers as described in claim 1 or 2 or 4 or 6 or 8 or 9 or 10, is characterized in that: described damper can resist axial impact and the radial impact of rotor-support-foundation system simultaneously.
13. dampers as described in claim 1 or 2 or 4 or 6 or 8 or 9 or 10, it is characterized in that: by adjusting the quantity of damping fin in the difference of circular diameter in the distance of single damping fin upper-end surface and lower end surface, upper-end surface outside diameter and lower end surface, damper, can the size of damping adjusting device damping ratio, with satisfied different supercharger rotor system to the requirement of damping ratio size.
14. dampers as claimed in claim 12, it is characterized in that: by adjusting the quantity of damping fin in the difference of circular diameter in the distance of single damping fin upper-end surface and lower end surface, upper-end surface outside diameter and lower end surface, damper, can the size of damping adjusting device damping ratio, with satisfied different supercharger rotor system to the requirement of damping ratio size.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410345024.0A CN104074553B (en) | 2014-07-18 | 2014-07-18 | A kind of turbosupercharger damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410345024.0A CN104074553B (en) | 2014-07-18 | 2014-07-18 | A kind of turbosupercharger damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104074553A CN104074553A (en) | 2014-10-01 |
| CN104074553B true CN104074553B (en) | 2015-11-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410345024.0A Active CN104074553B (en) | 2014-07-18 | 2014-07-18 | A kind of turbosupercharger damper |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2712951A1 (en) * | 1993-11-26 | 1995-06-02 | Fichtel & Sachs Ag | Axially tightened friction ring torsional oscillation damper in a motor vehicle transmission. |
| DE4336559A1 (en) * | 1993-10-27 | 1995-06-08 | Freudenberg Carl Fa | Vibration damper with rotary axle |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7597029B2 (en) * | 2002-10-15 | 2009-10-06 | International Engine Intellectual Property Company Llc | Damper assembly with reinforcing plate |
| KR20090040096A (en) * | 2007-10-19 | 2009-04-23 | 현대자동차주식회사 | Turbocharger of cng engine |
-
2014
- 2014-07-18 CN CN201410345024.0A patent/CN104074553B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4336559A1 (en) * | 1993-10-27 | 1995-06-08 | Freudenberg Carl Fa | Vibration damper with rotary axle |
| FR2712951A1 (en) * | 1993-11-26 | 1995-06-02 | Fichtel & Sachs Ag | Axially tightened friction ring torsional oscillation damper in a motor vehicle transmission. |
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| Publication number | Publication date |
|---|---|
| CN104074553A (en) | 2014-10-01 |
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Address after: 100191, Beijing, Xueyuan Road, Haidian District Patent Office 37 Yang Tingnan turn Applicant after: Beihang University Address before: 100191 Haidian District, Xueyuan Road, No. 37, Applicant before: Beihang University |
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Effective date of registration: 20210618 Address after: No. 1809-03, unit 2, 18 / F, building 2, 87 Jiancai Chengxi Road, Changping District, Beijing 100096 Patentee after: Beijing Keqi future technology development Co.,Ltd. Address before: 100191 No. 37, Haidian District, Beijing, Xueyuan Road Patentee before: BEIHANG University |
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Effective date of registration: 20220125 Address after: 100080 d4112, 4 / F, block D, Zhizhen building, No. 7, Zhichun Road, Haidian District, Beijing Patentee after: Beijing Lingdong Guochuang Technology Co.,Ltd. Address before: No. 1809-03, unit 2, 18 / F, building 2, 87 Jiancai Chengxi Road, Changping District, Beijing 100096 Patentee before: Beijing Keqi future technology development Co.,Ltd. |