CN104074553A - Damper for turbine supercharger - Google Patents
Damper for turbine supercharger Download PDFInfo
- Publication number
- CN104074553A CN104074553A CN201410345024.0A CN201410345024A CN104074553A CN 104074553 A CN104074553 A CN 104074553A CN 201410345024 A CN201410345024 A CN 201410345024A CN 104074553 A CN104074553 A CN 104074553A
- Authority
- CN
- China
- Prior art keywords
- end surface
- damper
- damping
- damping fin
- fin
- 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.)
- Granted
Links
Landscapes
- Supercharger (AREA)
Abstract
The invention discloses a damper in turbine supercharger rotor systems. The damper can simultaneously resist axial impact and radial impact, is adjustable in damping ratio, can meet the requirements of different supercharger rotor systems on the size of the damping ratio, weakens the vibration of the supercharger rotor systems, enlarges the application range of a supercharger, and belongs to the field of turbine superchargers. The damper comprises a group of damping sheets with special shapes, and the number of the damping sheets can be adjusted on the basis of the requirements of the supercharger rotor systems on the damping ratio.
Description
Technical field
The present invention proposes the damper in a kind of turbocharger rotor system, for reducing the vibration of supercharger rotor system, improves the anti-axial impact of rotor-support-foundation system and radial impact ability, belongs to field of turbochargers.
Background technique
Turbosupercharger, day by day towards precise treatment future development, in order to adapt to the variation of engine operating condition, reduces the vibration of supercharger rotor system, improves 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 to need special damper opposing to impact.General damper is divided into axial damper and two kinds of dampers radially, and rotor-support-foundation system will be resisted axial impact needs axial damper, and opposing impact radially needs radially 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, can meets the requirement of different supercharger rotor systems to 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, the damping fin that comprises 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 and bearing support of turbosupercharger, 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 be through machining, ensures planeness separately and the parallelism of upper and lower end face.
Further, damping fin thickness is 0.3～0.8mm, preferably 0.5mm; The distance of damping fin upper-end surface and lower end surface is 0.8～1.5mm, preferably 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 inclined-plane contact of adjacent two dampers, upper and lower end face does not all contact.
In the time that 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.
In the time that 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, damper of circular diameter in distance, upper-end surface outside diameter and the lower end surface of single damping fin upper-end surface and lower end surface, size that can damping adjusting device damping ratio, to meet the requirement of different supercharger rotor systems to damping ratio size.
In damper damping fin number, required comprehensively to determine by the distance between ball bearing and bearing support, system damping rate size and ball bearing play.
The invention has the advantages that:
1, this damper can be resisted axial impact and the radial impact of rotor-support-foundation system simultaneously;
2, the damping ratio of damper is adjustable, can meet the requirement of different supercharger rotor systems to damping ratio size;
3, simple in structure, be convenient to processing.
Brief description of the drawings
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 application of the present invention;
In figure:
1-damping fin 1 2-damping fin 2 3-damping fin 3 4-damping fins 4
5-damping fin 5 6-bearing support 7-damper 8-ball bearings
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, can meets the requirement of different supercharger rotor systems to 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, the damping fin that comprises one group of special shape, the quantity of one group of damping fin, can be according to the requirement adjustment 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.In the time that 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.In the time that 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, damper of circular diameter in distance, upper-end surface outside diameter and the lower end surface of single damping fin upper-end surface and lower end surface, size that can damping adjusting device damping ratio, to meet the requirement of different supercharger rotor systems to damping ratio size.
In damper damping fin number, required comprehensively to determine by the distance between ball bearing and bearing support, system damping rate size and ball bearing play.
Claims (8)
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.
2. damper as claimed in claim 1, is characterized in that: damping fin is made up of spring steel.
3. the damper as described in claim 1-2, is characterized in that: damping fin thickness is 0.3～0.8mm, preferably 0.5mm; The distance of damping fin upper-end surface and lower end surface is 0.8～1.5mm, preferably 1mm.
4. the damper as described in claim 1-3, is characterized in that: 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.
5. the damper as described in claim 1-4, is characterized in that: described damper is arranged between the ball bearing and bearing support of turbosupercharger, and carries out pretension by the nut of supercharger rotor system.
6. the damper as described in claim 1-5, 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, described quantity is 5～15, preferably 8.
7. the damper as described in claim 1-6, is characterized in that: described damper can be resisted axial impact and the radial impact of rotor-support-foundation system simultaneously.
8. the damper as described in claim 1-7, it is characterized in that: by adjusting the quantity of damping fin in the difference, damper of circular diameter in distance, upper-end surface outside diameter and the lower end surface of single damping fin upper-end surface and lower end surface, size that can damping adjusting device damping ratio, to meet the requirement of different supercharger rotor systems to 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 true CN104074553A (en) | 2014-10-01 |
| CN104074553B CN104074553B (en) | 2015-11-04 |
Family
ID=51596119
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 |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104074553B (en) |
Citations (4)
| 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 |
| US20040069093A1 (en) * | 2002-10-15 | 2004-04-15 | Bernard Jeremy R. | 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 (4)
| 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. |
| US20040069093A1 (en) * | 2002-10-15 | 2004-04-15 | Bernard Jeremy R. | Damper assembly with reinforcing plate |
| KR20090040096A (en) * | 2007-10-19 | 2009-04-23 | 현대자동차주식회사 | Turbocharger of cng engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104074553B (en) | 2015-11-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2009079628A5 (en) | ||
| EP2565394A3 (en) | Annular bearing support dampers, gas turbine engines including the same, and methods for the manufacture thereof | |
| WO2015175962A1 (en) | Air foil bearings having multiple pads | |
| EP2290198A3 (en) | Bearing spacer and housing | |
| EP2378064A3 (en) | Axial turbine | |
| CN105683502A (en) | Rotating body and method for manufacturing rotating body | |
| EP2871324A3 (en) | Axial turbine with an adjustable guide plate | |
| CN102788114A (en) | Variable radius engine crankshaft balancing mechanism | |
| EP2743456A3 (en) | Multiple scroll turbocharger | |
| EP2639403A3 (en) | Shaft Assembly for a Gas Turbine Engine | |
| CN104074553B (en) | A kind of turbosupercharger damper | |
| CN104389850B (en) | Oil cylinder with floating buffer structure | |
| CN101799044B (en) | Series electromagnetic-elastic foil combined bearing | |
| CN204458789U (en) | The angled type reciprocating-piston compressor that a kind of balance of shaking force is optimized | |
| US9915152B2 (en) | Turbine wheel | |
| CN206216288U (en) | Cam-type retaining mechanism | |
| CN109139793B (en) | Nonlinear vibration absorber with multistable rigidity | |
| CN102635495B (en) | Automatic pitch-adjusting wind wheel | |
| CN203092326U (en) | Precision grinding head | |
| CN106499764B (en) | A kind of rigidity mutation impact resisting vibrating damper | |
| CN205309748U (en) | Tapered roller bearing play is adjusted structure | |
| US20160146047A1 (en) | Turbocharger roller support system | |
| CN102705370A (en) | Design mounting method for assembled angular contact ball bearing with outer ring having double rolling passages | |
| CN204212816U (en) | A kind of half wheel disc turbine | |
| WO2017054927A3 (en) | Tensioning unit for rolling bearings on axles and shafts |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB02 | Change of applicant information |
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 |
|
| COR | Change of bibliographic data | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
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 |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
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. |