CN101571056B - Miniature rotor dynamic mechanical damping structure - Google Patents
Miniature rotor dynamic mechanical damping structure Download PDFInfo
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- CN101571056B CN101571056B CN2009100861512A CN200910086151A CN101571056B CN 101571056 B CN101571056 B CN 101571056B CN 2009100861512 A CN2009100861512 A CN 2009100861512A CN 200910086151 A CN200910086151 A CN 200910086151A CN 101571056 B CN101571056 B CN 101571056B
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- friction plate
- disc spring
- spring friction
- thin
- damping structure
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Abstract
The invention discloses a miniature rotor dynamic mechanical damping structure. The damping structure comprises a disc spring friction plate and a thin-walled elastic bearing base; the disc spring friction plate is arranged between an air compressor impeller and a turbine, an inner ring and a rotary shaft are in clearance fit, an outer ring and a shell body force bearing part are in interference fit; the thin-walled elastic bearing base is arranged at the outer ring of a bearing at the end of the turbine, the inner ring and the bearing are in interference fit, and the outer ring and the shell body force-bearing part are in interference fit. The damping structure has simple structural form, low cost, simple installation and obvious damping effect on a 1-O-1 type rotor support structure and can effectively control the vibration amplitude of a miniature turbojet engine and a gas turbine at high rotation speed.
Description
Technical field
The invention belongs to the miniature rotor dynamic mechanical damping technical field, relate to a kind of miniature rotor dynamic mechanical damping structure, specifically, be meant a kind of vibration damping equipment that is used in jet engine of microminiature turbine or the miniature gas turbine.
Background technique
Micro Turbine Jet Engine and micro fuel engine are the aviation and the distributed energy power plant of state key research and development over past ten years.Its main structure characteristics are that volume is little, rotating speed is high, and the vibration control problem under the high rotating speed of the rotor that brings thus is the key factor that influences whole aircraft reliability.Present existing damping technology comprises: elastic support, squeeze film damper, metal-rubber damper, magnetic bearing, foil bearing and dry friction damping technology etc.Characteristics such as wherein, relative other vibration reducing measure of dry friction damping technology has simple in structure, need not annex, and cost is low, and form is flexible, and is easy for installation.Especially in recent years, be used widely in a plurality of fields.In the aeroengine field, domestic certain institute proposed sound formula dry friction damping technology.Its structure is that two friction plate one are fixed, and another sheet rotates with rotating shaft, and two friction plates produce relative movement during rotor oscillation, thereby the dissipates vibration energy reaches the purpose of vibration damping.The frictional force size is by the positive pressure adjustment between two friction plates that initially provide.This structural validation the validity of dry friction vibration damping, but application remain the test.Different supporting structures is proposed more effectively vibration reducing measure, and standardization, modularization that miniature rotor dynamic mechanical is designed have positive promoting effect.Structure of the present invention proposes at 1-0-1 formula supporting structure in the miniature rotor power plant, is fit to engineering and uses, in microvovtex spray of grinding and combustion machine project reference function being arranged at present.
Summary of the invention
Purpose of the present invention is to lack at domestic miniature rotor power plant design experiences, and vibration damping structure designs incomplete characteristics, and a kind of miniature rotor dynamic mechanical damping structure scheme is provided.Described vibration damping structure proposes at 1-0-1 formula rotor supports mode, and the disc spring friction plate group is installed between compressor impeller and turbine, at the turbine end bearing outer ring thin-walled elastic axis bearing is installed, to reach the purpose of vibration damping, enhancing rotor stability.
Vibration damping structure of the present invention comprises disc spring friction plate group and thin-walled elastic axis bearing; Described disc spring friction plate group is installed between compressor impeller and the turbine, and inner ring and rotating shaft are Spielpassung, and outer ring and housing load spare are interference fit; Described thin-walled elastic axis bearing is installed in the turbine end bearing outer ring, and inner ring and bearing are interference fit, and outer ring and housing load spare are interference fit.Disc spring friction plate is divided two groups of opposed installations, every group can comprise one or more disc spring friction plate, and concrete quantity depends on the needs, and contacts with each other between every group of friction plate inner and outer surface, limit its axial motion degrees of freedom by housing load spare, so that remain contact condition between each friction plate.The principle of two groups of opposed modes of disc spring friction plate is: the volume maximum that disc spring friction plate, rotating shaft, housing load spare three are surrounded, and for cooling air provides enough spaces.Two groups of disc spring friction plate play the effect of supplemental support and dissipates vibration energy simultaneously.Thin-walled elastic axis bearing provides bigger flexibility for the turbine end bearing, and the damping that the bearing oil around cooperating provides helps strain energy release and vibrational energy and dissipates.
During working rotor, mass concentration between two bearings makes initial bending bigger to the dynamic characteristic influence.The integral rigidity of disc spring friction plate group is bigger, cooperates bearings at both ends to play the supplemental support effect, reduces initial bending, has also suppressed lateral amplitude of vibration simultaneously, the dry friction effective attenuation that provides between friction plate vibrational energy, but also have stronger strain energy.Reduce the turbine end bearing rigidity by thin-walled elastic axis bearing, for the release of strain energy provides condition.The existence of lubricant oil around the bearing support makes the vibration that produces when strain energy discharges decay rapidly.
Advantage of the present invention:
(1) vibration damping structure provided by the invention has advantage simple in structure, that cost is low.
(2) vibration damping structure of this invention is with strong points, effectiveness in vibration suppression obvious, be fit to engineering uses.
Description of drawings
Fig. 1 is equipped with the 1-0-1 formula support rotor system architecture schematic representation of vibration damping structure;
Fig. 2 rotor-support-foundation system longitudinal section;
Fig. 3 disc spring friction plate group structural representation;
Fig. 4 disc spring friction plate sectional drawing;
Fig. 5 is the partial enlarged drawing of Fig. 2.
Embodiment
The present invention will be further described below in conjunction with accompanying drawing.
The invention provides a kind of miniature rotor dynamic mechanical damping structure, described vibration damping structure is installed on the 1-0-1 support rotor structure, as shown in Figure 1 and Figure 2, described vibration damping structure comprises disc spring friction plate group 4 and thin-walled elastic axis bearing 7, disc spring friction plate group 4 is installed in the rotating shaft 1 between compressor impeller 3 and the turbine 5, and particular location is determined according to the rotor-support-foundation system specific constructive form and the rotor vibration shape.Thin-walled elastic axis bearing 7 is installed in the outer ring of rear end bearing 6, and assembly relation is an interference fit.
The structure of described disc spring friction plate group 4 as shown in Figure 3, left side disc spring friction plate group 401 and the 402 opposed installations of right disc spring friction plate group, opposed installation principle is the space maximum that makes between left disc spring friction plate group 401 and the right disc spring friction plate group 402.Disc spring friction plate sectional view as shown in Figure 4, lobed outer surface 405 of disc spring friction plate and recessed internal surface 406, when disc spring friction plate is installed, two groups of disc spring friction plate internal surfaces 406 are installed relatively, it is the distance maximum between the outer surface 405, distance between the internal surface 406 is minimum, and the outer surface 405 that also is left disc spring friction plate group 401 is towards the left side, and the outer surface 405 of right disc spring friction plate group 402 is towards the right side.The inner ring 407 and the rotating shaft 1 of left side disc spring friction plate group 401 and right disc spring friction plate group 402 are Spielpassung, outer ring 408 is an interference fit with housing load spare 403, by the draw-in groove 404 left disc spring friction plate groups 401 of restriction of housing load spare 403 and the axial displacement of right disc spring friction plate group 402.Described left disc spring friction plate group 401 and right disc spring friction plate group 402 can comprise one or more disc spring friction plate respectively, and concrete quantity can just be adjusted according to level of vibration.
The structure of described thin-walled elastic axis bearing 7 as shown in Figure 4, thin-walled elastic axis bearing 7 is an interference fit with rear end bearing 6, its structural type is annular thin wall part.The length of thin-walled elastic axis bearing 7 and rear end bearing 6 contact-segments has determined the size of rear end support stiffness, packing lubrication oil between thin-walled elastic axis bearing 7 and the rear end bearing 6, and the size of bearing lubrication oil viscosity and oil pressure has determined the size of damping.
The integral rigidity of disc spring friction plate group 4 is bigger, and step bearing 2 and rear end bearing 6 play the supplemental support effect before cooperating, and reduce initial bending, has also suppressed the rotor lateral amplitude of vibration simultaneously, the dry friction effective attenuation that provides between friction plate vibrational energy.Reduce the rigidity of rear end bearings 6 by thin-walled elastic axis bearing 7, for the release of strain energy provides condition.The existence of lubricant oil around the thin-walled elastic axis bearing 7 makes the vibration that produces when strain energy discharges decay rapidly.
Claims (3)
1. miniature rotor dynamic mechanical damping structure, it is characterized in that: described vibration damping structure is at 1-0-1 formula rotor supports mode, and described vibration damping structure comprises disc spring friction plate group and thin-walled elastic axis bearing; Described disc spring friction plate group is installed between compressor impeller and the turbine, disc spring friction plate group inner ring and rotating shaft are Spielpassung, disc spring friction plate group outer ring and housing load spare are interference fit, the axial displacement of the draw-in groove restriction disc spring friction plate group of housing load spare; Described thin-walled elastic axis bearing is installed in the turbine end bearing outer ring, and thin-walled elastic axis bearing inner ring and turbine end bearing outer ring are interference fit, and thin-walled elastic axis bearing outer ring and housing load spare are interference fit; Two groups of opposed installations of described disc spring friction plate component, the principle of described opposed installation is: the volume maximum that disc spring friction plate group, rotating shaft, housing load spare three are surrounded, for cooling air provides enough spaces, the structural type of described thin-walled elastic axis bearing is annular thin wall part, packing lubrication oil between thin-walled elastic axis bearing and the turbine end bearing.
2. a kind of miniature rotor dynamic mechanical damping structure according to claim 1, it is characterized in that: described disc spring friction plate group, every group comprises an above disc spring friction plate, contacts with each other between the friction plate inner and outer surface, limits its axial motion degrees of freedom by housing load spare.
3. a kind of miniature rotor dynamic mechanical damping structure according to claim 2, it is characterized in that: described two groups of disc spring friction plate internal surfaces are installed relatively, be that distance between the outer surface is big, distance between the internal surface is little, described outer surface is meant the convex surface of disc spring friction plate, and described internal surface is meant the concave surface of disc spring friction plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100861512A CN101571056B (en) | 2009-06-09 | 2009-06-09 | Miniature rotor dynamic mechanical damping structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100861512A CN101571056B (en) | 2009-06-09 | 2009-06-09 | Miniature rotor dynamic mechanical damping structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101571056A CN101571056A (en) | 2009-11-04 |
| CN101571056B true CN101571056B (en) | 2011-05-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100861512A Expired - Fee Related CN101571056B (en) | 2009-06-09 | 2009-06-09 | Miniature rotor dynamic mechanical damping structure |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102720787B (en) * | 2012-06-12 | 2013-11-06 | 中国科学院工程热物理研究所 | Multilayer-laminated damper |
| CN103671221A (en) * | 2012-09-10 | 2014-03-26 | 刘大刚 | Elastic supporting fan |
| US10677312B2 (en) * | 2018-02-15 | 2020-06-09 | General Electric Company | Friction shaft damper for axial vibration mode |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1544821A (en) * | 2003-11-14 | 2004-11-10 | 清华大学 | Electromagnetic bearing protecting equipment |
| CN201025157Y (en) * | 2007-02-12 | 2008-02-20 | 深圳市康铖机械设备有限公司 | Micro turbine jet engine |
| CN201053353Y (en) * | 2006-12-29 | 2008-04-30 | 深圳市康铖机械设备有限公司 | Mini turbine jet engine |
-
2009
- 2009-06-09 CN CN2009100861512A patent/CN101571056B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1544821A (en) * | 2003-11-14 | 2004-11-10 | 清华大学 | Electromagnetic bearing protecting equipment |
| CN201053353Y (en) * | 2006-12-29 | 2008-04-30 | 深圳市康铖机械设备有限公司 | Mini turbine jet engine |
| CN201025157Y (en) * | 2007-02-12 | 2008-02-20 | 深圳市康铖机械设备有限公司 | Micro turbine jet engine |
Non-Patent Citations (1)
| Title |
|---|
| 陈巍，杜发荣，丁水汀，李云清.微型涡喷发动机转子系统设计.《航空动力学报》.2009,第24卷(第5期),1171-1176. * |
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| CN101571056A (en) | 2009-11-04 |
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Granted publication date: 20110518 Termination date: 20120609 |