CN205047663U - Rotor support structure - Google Patents
Rotor support structure Download PDFInfo
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- CN205047663U CN205047663U CN201520672257.1U CN201520672257U CN205047663U CN 205047663 U CN205047663 U CN 205047663U CN 201520672257 U CN201520672257 U CN 201520672257U CN 205047663 U CN205047663 U CN 205047663U
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- bearing
- support structure
- ripple spring
- rotor support
- aperture
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Abstract
The utility model provides a rotor support structure, include: the bearing mount pad, and install the bearing in this bearing mount pad, this contracting draws together bearing inner ring, bearing outer ring and be located this bearing inner ring and this bearing outer ring between the ball, wherein, the cover has the ripples spring between this bearing mount pad and this bearing outer ring, this ripples spring upwards presents continuous undulation along the circumference in the footpath and hugs closely the crest of this bearing mount pad and the trough of hugging closely this bearing outer ring with formation, thereby separate to become this bearing mount pad and the clearance between this bearing outer ring along a plurality of cavitys of circumference, be full of lubricating oil and sealed through installing in the sealing ring at axial both ends in these a plurality of cavitys.
Description
Technical field
The utility model relates to engine rotor technology, particularly relates to a kind of rotor support structure.
Background technique
Aero gas turbine engine rotor is all supported on casing with rolling bearing.Because rolling bearing damping is very little, negligible, and be directly contained on casing bearing support.During engine operation, the unbalanced force of rotor passes to casing by supporting structure, makes engine causes vibration.In addition, rolling bearing can not the vibration of effective attenuation rotor by producing during cal speed.In order to reduce engine luggine, improving engine life, between the outer race and bearing support of some supporting place, adopting elastic support structure and squeeze film damper.
Squeeze film damper extrudes the lubricating oil around it by bearing, forms oil film, and produces damping vibration attenuation function by hydrodynamic, reduces vibration thus.Usually elastic support structure and squeeze film damper are installed in parallel on casing, utilize elastic support structure to feel relieved; Utilize squeeze film damper attenuation vibration.But traditional elastic supporting structure and squeeze film damper adhere to two different structures separately, occupy more space, squeeze film damper structure also slightly complicated.Meanwhile, when bearing is larger relative to the eccentricity of casing, namely axle journal is amesiality, and the characteristic of squeeze film damper becomes particularly complicated, brings many difficult points to design.Therefore, above-mentioned yielding support and squeeze film damper only use to some extent in Main Shaft Bearing of Engine, and usually also need the maximum eccentric rate limiting axle journal, to ensure the authentic and valid of squeeze film damper design parameter.
Traditional elastic support structure and squeeze film damper can not be used for other rotatable parts outside engine spindle, and no longer adapt to the requirement of present engine miniaturization and compact design gradually, new structure need be used the two to be combined together, need again to ensure that there is the rigidity suitable with conventional construction and damping characteristic simultaneously.
Model utility content
In order to overcome above-mentioned defect, the utility model aims to provide a kind of rotor support structure.
According to one side of the present utility model, provide a kind of rotor support structure, comprising:
Bearing mounting base; And
Be arranged on the bearing in this bearing mounting base, this bearing comprises bearing inner ring, outer race and the ball between this bearing inner ring and this outer race,
Wherein, overlap between this bearing mounting base and this outer race and have ripple spring, this ripple spring circumferentially presents fluctuating continuously diametrically and is close to the crest of this bearing mounting base to be formed and is close to the trough of this outer race, thus the separated between this bearing mounting base with this outer race is become multiple cavitys circumferentially, be full of lubricating oil in the plurality of cavity and seal ring seal by being installed on axial two ends.
In one example, this ripple spring is circumferentially distributed with the aperture of penetrated wave spring thickness, and to make to be communicated with between the plurality of cavity, thus lubricating oil can flow between each cavity via aperture.
In one example, the bearing of trend of this aperture is vertical with ripple spring surface, to form the runner passing perpendicularly through ripple spring thickness.
In one example, the bearing of trend of this aperture favours ripple spring surface, to form the runner of ripple spring thickness athwart.
In one example, this aperture extends through ripple spring thickness, to form bending runner along bending circuit.
In one example, the number of this aperture and diameter depend on required damping size.
In one example, this ripple spring is made by increasing material processing technology one-body moldedly.
By rotor support structure of the present utility model, bearing is under the effect of rotor unbalance power, lubricating oil and ripple spring is extruded when outer hoop unbalanced force direction is moved, play the effect of restriction outer race movement on the one hand, also absorb the energy of external rotor vibration simultaneously, reduce rotor bearing rigidity, the Joint effect reducing rotor bearing rigidity and increase damping can be taken into account.Meanwhile, rotor support structure of the present utility model is simple, take axial, radial space is little, good damping result, be adapted at any rotor support structure uses.
In brief, this rotor support structure, both by elastic element adjustment rotor critical speed, reduces again the structure of the unofficial biography vibration of rotor, simultaneously by damping member, this structure simple optimizing as far as possible, can be able to realize under the prerequisite not changing existing rotor support structure space.
Accompanying drawing explanation
After the detailed description of reading embodiment of the present disclosure in conjunction with the following drawings, more can understand above-mentioned feature and advantage of the present utility model better.
Fig. 1 shows the plan view of the rotor support structure according to one side of the present utility model;
Fig. 2 shows the generalized section along A-A line in Fig. 1;
Fig. 3 A-3C shows the schematic diagram according to the aperture on the ripple spring of one side of the present utility model.
For clarity sake, the brief description of reference character is below provided:
100: rotor support structure
101: bearing mounting base
102: seal ring
103: ripple spring 1031: cavity 1032: aperture
104: outer race
105: ball
106: bearing inner ring
107: rotor
Embodiment
Below in conjunction with the drawings and specific embodiments, the utility model is described in detail.Note, the aspects described below in conjunction with the drawings and specific embodiments is only exemplary, and should not be understood to carry out any restriction to protection domain of the present utility model.
Fig. 1 shows the plan view of the rotor support structure 100 according to one side of the present utility model, and Fig. 2 shows the generalized section along A-A line in Fig. 1.The structure of rotor support structure 100 can be clearly shown that from the combination of Fig. 1 and Fig. 2.
As shown in Figure 1, rotor support structure 100 can comprise bearing mounting base 101 and bearing.Bearing can comprise bearing outer wall 104, bearing inner wall 106 and the ball between both 105.Rotor 107, i.e. running shaft, through the ring heart of bearing inner wall 106.Left and right directions in Fig. 1 is axial direction, and above-below direction is radial direction.
Space between bearing mounting base 101 and bearing outer wall 104, is provided with ripple spring 103.This ripple spring 103 is made up of the reed of ring-type, thus is enclosed within outside bearing outer wall 104 and within bearing mounting base 101.The reed of ripple spring 103 is along with circumferentially extending, and present continuous fluctuating diametrically, thus form a series of crest and trough, bearing mounting base 101 is close at crest position, and bearing outer wall 104 is close at trough position.Thus, the annulus between bearing mounting base 101 and bearing outer wall 104 is split into multiple independently cavity 1031, and these cavitys 1031 circumferentially distribute successively.
In these cavitys 1031, be filled with lubricating oil, these lubricating oil are sealed in the space between bearing mounting base 101 and bearing outer wall 104 by the seal ring 102 being installed on axially two ends.
Thus, in the radial gap of ripple spring 103 between outer race 104 and bearing mounting base 101, can ensure that bearing and rotor 107 are relative to the centering requirement of bearing mounting base 101, also can realize the yielding support in small space and centering function.
Ripple spring 103 can support in the all-round scope of outer race 104, ensures to have the function of centering spring by the range of motion that bearing and the rotor journal supported by bearing are being permitted.Lubricating oil between outer race 104 and bearing mounting base 101 plays damping function, can reduce vibrational loading and the amplitude of rotor unofficial biography, reduces engine luggine.Ripple spring 103 limits outer race 104 and moves, and can realize larger radial displacement, and change rotor 107 supporting rigidity, make rotor 107 become flexible rotor, engine operation is under supercritical speed, and stable working, vibrates little simultaneously.
More preferably, ripple spring 103 circumferentially has multiple aperture 1032, the reed thickness of these aperture 1032 penetrated wave springs 103, thus makes to be communicated with each other by corresponding aperture 1032 between these cavitys 1031 circumferential.Under this arrangement, lubricating oil can flow between each cavity 1031 via aperture 1032.
The unbalanced force load coming from rotor 107 makes outer race 104 produce radial displacement relative to bearing mounting base 101, and ripple spring 103 bears produced displacement and deforms, and the volume of cavity 1031 is changed.Therefore lubricating oil in cavity 1031 is flowed in each cavity 1031 by the aperture 1032 be opened on ripple spring 103, utilizes throttle effect to produce damping.Utilize throttle effect to produce damping, significantly reduce lubricating oil charge oil pressure and traffic requirement.And, be enclosed construction due to what adopt, significantly reduce lubricating oil demand.
The distortion of ripple spring 103 limits the radial displacement of outer race 104, and then limits the axle center locus of rotor 107.The throttle effect that lubricating oil in cavity 1031 flows through aperture 1032 generation absorbs the vibration coming from rotor 107, plays the effect of vibration damping, thus minimizing is vibrated the unofficial biography of bearing mounting base 101.
The function of damping adjusting can be realized, to meet the needs of different rotor supporting system by the diameter or quantity regulating the aperture 1032 that ripple spring 103 is offered.
Especially, according to requirements, by changing the direction of the aperture 1032 that ripple spring 103 is offered, ripple spring 103 being formed the longer elongated hole of runner or the shorter short-bore of runner, by changing the flow channel length of aperture 1032, thus changing damping size.
Such as in the example shown in Fig. 3 A, the bearing of trend of aperture 1032a favours ripple spring surface, namely the bearing of trend of aperture 1032a and this ripple spring normal to a surface direction, aperture place are an angle, so form the runner of ripple spring thickness athwart, such runner is longer.In the example shown in Fig. 3 A, the bearing of trend of aperture 1032b is vertical with ripple spring surface, and to form the runner passing perpendicularly through ripple spring thickness, such runner is longer.By changing the flow channel length of aperture 1032, can damping adjusting size.
Fig. 3 C shows the another kind configuration of aperture, such as aperture 1032c, and as shown in the figure, aperture 1032c extends through ripple spring thickness along bending circuit, thus defines bending runner.This can increase damping, meets the needs of large damping support.
In actual use, the ripple spring of aperture offering different-diameter, varying number, different direction, different longitudinal cross-sections shape can be changed as required, thus reach the object of damping adjusting.
In practice, ripple spring 103 by increase material processing technology one-body molded make, solve the problem of circumference ripple spring difficult processing like this, and the accuracy of manufacturing of the complex-curved structure of ripple spring can be ensured.Meanwhile, on ripple spring 103, directly can generate different pore size, direction, even bending lubricating oil runner, realize different damping sizes.
By rotor support structure of the present utility model, bearing is under the effect of rotor unbalance power, lubricating oil and ripple spring is extruded when outer hoop unbalanced force direction is moved, play the effect of restriction outer race movement on the one hand, also absorb the energy of external rotor vibration simultaneously, reduce rotor bearing rigidity, the Joint effect reducing rotor bearing rigidity and increase damping can be taken into account.Meanwhile, rotor support structure of the present utility model is simple, take axial, radial space is little, good damping result, be adapted at any rotor support structure uses.
In brief, this rotor support structure, both by elastic element adjustment rotor critical speed, reduces again the structure of the unofficial biography vibration of rotor, simultaneously by damping member, this structure simple optimizing as far as possible, can be able to realize under the prerequisite not changing existing rotor support structure space.
Description before providing is to make any technician in related domain all can put into practice various aspects described herein.But should be appreciated that, protection domain of the present utility model should be as the criterion with claims, and should not be defined to concrete structure and the assembly of above explained orally embodiment.Those skilled in the art, in spirit and scope of the present utility model, can carry out various variation and amendment to each embodiment, and these variations and amendment also drop within protection domain of the present utility model.
Claims (7)
1. a rotor support structure, is characterized in that, comprising:
Bearing mounting base; And
Be arranged on the bearing in described bearing mounting base, described bearing comprises bearing inner ring, outer race and the ball between described bearing inner ring and described outer race,
Wherein, overlap between described bearing mounting base and described outer race and have ripple spring, described ripple spring circumferentially presents fluctuating continuously diametrically and is close to the crest of described bearing mounting base to be formed and is close to the trough of described outer race, thus the separated between described bearing mounting base with described outer race is become multiple cavitys circumferentially, be full of lubricating oil in described multiple cavity and seal ring seal by being installed on axial two ends.
2. rotor support structure as claimed in claim 1, it is characterized in that, described ripple spring is circumferentially distributed with the aperture of penetrated wave spring thickness, and to make to be communicated with between described multiple cavity, thus lubricating oil can flow between each cavity via aperture.
3. rotor support structure as claimed in claim 2, is characterized in that, the bearing of trend of described aperture is vertical with ripple spring surface, to form the runner passing perpendicularly through ripple spring thickness.
4. rotor support structure as claimed in claim 2, is characterized in that, the bearing of trend of described aperture favours ripple spring surface, to form the runner of ripple spring thickness athwart.
5. rotor support structure as claimed in claim 2, is characterized in that, described aperture extends through ripple spring thickness, to form bending runner along bending circuit.
6. rotor support structure as claimed in claim 2, it is characterized in that, the number of described aperture and diameter depend on required damping size.
7. the rotor support structure according to any one of claim 1-6, is characterized in that, described ripple spring is made by increasing material processing technology one-body moldedly.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520672257.1U CN205047663U (en) | 2015-09-01 | 2015-09-01 | Rotor support structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520672257.1U CN205047663U (en) | 2015-09-01 | 2015-09-01 | Rotor support structure |
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| Publication Number | Publication Date |
|---|---|
| CN205047663U true CN205047663U (en) | 2016-02-24 |
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| CN201520672257.1U Active CN205047663U (en) | 2015-09-01 | 2015-09-01 | Rotor support structure |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106015315A (en) * | 2016-08-04 | 2016-10-12 | 江苏亚星波纹管有限公司 | Corrugated tube bearing device |
| CN106015326A (en) * | 2016-07-11 | 2016-10-12 | 欧献忠 | Bearing |
| CN106594068A (en) * | 2017-01-23 | 2017-04-26 | 宁波银球小型轴承有限公司 | Deep groove ball bearing damping ring suitable for air conditioning compressor and deep groove ball bearing |
| CN108150605A (en) * | 2017-12-18 | 2018-06-12 | 北京大块科技有限公司 | A kind of damping shock absorber and its manufacturing method |
| CN110925299A (en) * | 2019-12-23 | 2020-03-27 | 河南澈蓝环保技术有限公司 | Flexible self-balancing noise reduction bearing |
| CN115111262A (en) * | 2022-07-04 | 2022-09-27 | 中国舰船研究设计中心 | Ship long shafting anti-impact protection device and design method thereof |
| CN115217878A (en) * | 2021-04-21 | 2022-10-21 | 中国航发商用航空发动机有限责任公司 | Squeeze film damper assembly and aircraft engine |
-
2015
- 2015-09-01 CN CN201520672257.1U patent/CN205047663U/en active Active
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106015326A (en) * | 2016-07-11 | 2016-10-12 | 欧献忠 | Bearing |
| CN106015315A (en) * | 2016-08-04 | 2016-10-12 | 江苏亚星波纹管有限公司 | Corrugated tube bearing device |
| CN108916220B (en) * | 2017-01-23 | 2020-04-03 | 郑梦兰 | Dedicated deep groove ball bearing damping ring of air condition compressor |
| CN106594068A (en) * | 2017-01-23 | 2017-04-26 | 宁波银球小型轴承有限公司 | Deep groove ball bearing damping ring suitable for air conditioning compressor and deep groove ball bearing |
| CN106594068B (en) * | 2017-01-23 | 2018-10-09 | 宁波银球小型轴承有限公司 | A kind of deep groove ball bearing shock ring and deep groove ball bearing suitable for compressor of air conditioner |
| CN108916220A (en) * | 2017-01-23 | 2018-11-30 | 宁波高新区起兴机电有限公司 | A kind of dedicated deep groove ball bearing shock ring of compressor of air conditioner |
| CN108916218A (en) * | 2017-01-23 | 2018-11-30 | 宁波高新区起兴机电有限公司 | A kind of bumper and absorbing shock ring for compressor of air conditioner deep groove ball bearing |
| CN108150605A (en) * | 2017-12-18 | 2018-06-12 | 北京大块科技有限公司 | A kind of damping shock absorber and its manufacturing method |
| CN110925299A (en) * | 2019-12-23 | 2020-03-27 | 河南澈蓝环保技术有限公司 | Flexible self-balancing noise reduction bearing |
| CN115217878A (en) * | 2021-04-21 | 2022-10-21 | 中国航发商用航空发动机有限责任公司 | Squeeze film damper assembly and aircraft engine |
| CN115217878B (en) * | 2021-04-21 | 2024-04-16 | 中国航发商用航空发动机有限责任公司 | Squeeze film damper assembly and aeroengine |
| CN115111262A (en) * | 2022-07-04 | 2022-09-27 | 中国舰船研究设计中心 | Ship long shafting anti-impact protection device and design method thereof |
| CN115111262B (en) * | 2022-07-04 | 2024-07-16 | 中国舰船研究设计中心 | Ship long shafting impact-resistant protection device and design method thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 200241 Minhang District Lianhua Road, Shanghai, No. 3998 Patentee after: China Hangfa commercial aviation engine limited liability company Address before: 200241 Minhang District Lianhua Road, Shanghai, No. 3998 Patentee before: AVIC Commercial Aircraft Engine Co.,Ltd. |
|
| CP01 | Change in the name or title of a patent holder |