CN204255625U - A kind of wheel rim centrifugal load model configuration for wheel disc test - Google Patents
A kind of wheel rim centrifugal load model configuration for wheel disc test Download PDFInfo
- Publication number
- CN204255625U CN204255625U CN201420706154.8U CN201420706154U CN204255625U CN 204255625 U CN204255625 U CN 204255625U CN 201420706154 U CN201420706154 U CN 201420706154U CN 204255625 U CN204255625 U CN 204255625U
- Authority
- CN
- China
- Prior art keywords
- wheel disc
- balancing weight
- wheel
- rim
- centrifugal load
- 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.)
- Active
Links
Landscapes
- Testing Of Balance (AREA)
Abstract
The utility model belongs to aeromotor wheel disk technology, relates to a kind of wheel rim centrifugal load model configuration for wheel disc test.The wheel rim centrifugal load model configuration that the utility model is used for wheel disc test is made up of balancing weight and wheel disc, described balancing weight is circumferential partitioned organization, be arranged on wheel disc outer rim, the position of balancing weight, quantity and structural parameters are regulated by design, realize the simulation to wheel disc centrifugal force, and significantly reduce experimentation cost.In addition, the utility model, by arranging balancing bolt mounting hole on balancing weight, effectively reduces vibration, improves test simulation effect, has larger economic benefit.
Description
Technical field
The utility model belongs to aeromotor wheel disk technology, relates to a kind of wheel rim centrifugal load model configuration for wheel disc test.
Background technology
In aeromotor, the function of wheel disc is steady job blade and passes on axle by the power that working-blade obtains, wheel disc mainly bears the huge centrifugal force of the structure such as working-blade, tongue and groove couplijng and disk body itself, and the thermal stress caused by disk body thermograde.Wheel disc is the vital part of aeromotor, and its destruction can cause the catastrophic failure of aircraft, so must avoid the inefficacy that wheel disc occurs.Therefore, wheel disc should have enough intensity, with bear the regulation such as airworthiness standard and GJB excess revolutions, break and the test condition such as fatigue.
Common wheel disc testpieces directly selects engine true zero parts, is made up of the part such as blade and wheel disc.Blade generally comprises blade, listrium and tenon first class sections, be arranged on the outer rim that the parts such as the blade on wheel disc are all positioned at wheel disc, in order to consider the centrifugal load that wheel disc outer rim is born, wheel disc to being processed the tongue and groove couplijng for installing blade, also needing to use the parts such as locking plate to be locked by blade in assembling.This wheel disc testpieces difficulty of processing is large, the process-cycle is long, and manufacturing cost is high.
Utility model content
The purpose of this utility model: under the utility model provides a kind of prerequisite not affecting disc strength certification test, effectively can reduce difficulty of processing, shorten the process-cycle, the wheel rim centrifugal load model configuration for wheel disc test of increasing economic efficiency.
The technical solution of the utility model: a kind of wheel rim centrifugal load model configuration for wheel disc test, it comprises balancing weight and wheel disc, and wherein, described balancing weight is circumferential partitioned organization, is arranged on wheel disc outer rim, and quantity is n
2, single balancing weight angle is circumferentially 360 °/n
2, described balancing weight is along the thickness L of wheel disc axis
1with true rim axle to consistency of thickness, balancing weight bottom radius R
1consistent with bottom true wheel disc chase mortise.
The distance of the peripheral boundaries of balancing weight and its cut-off rule is L
2, the peripheral boundaries distance between adjacent two balancing weights is 2L
2.
Described L
2span be the radial height H of 1 ~ 1.5mm, balancing weight
1span be no more than R
2-(R
1+ 2R
3), wherein, n
2be no more than number of blade n
1, R
2for the tip radlus of wheel disc, R
3for compensating groove arc radius.
Described balancing weight root is provided with compensating groove.
Described balancing weight is designed with balancing bolt mounting hole along the thickness direction of wheel disc axis.
The radius of balancing bolt mounting hole is R
4, each balancing weight center line arranges one, is 180 °/n with the angle of balancing weight cut-off rule
2, radius R
4span is 2.5 ~ 3.0mm.
Balancing bolt mounting hole is (R along the mobile space of wheel disc radial direction
1+ 2R
3) ~ (R
1+ 2R
3+ H
1).
The beneficial effects of the utility model: the utility model is used for the wheel rim centrifugal load model configuration of wheel disc test, adopt balancing weight to replace the structure such as real blade, tongue and groove couplijng, and can simulate the actual centrifugal load on wheel rim comparatively really.Owing to adopting the wheel disc testpieces of balancing weight, structure is simple, and decrease number of parts, reliability is high, and does not need real blade, therefore effectively reduces testpieces difficulty of processing, and the process-cycle shortens, and significantly reduces experimentation cost, creates larger economic benefit.
Accompanying drawing explanation
Fig. 1 is the wheel rim centrifugal load model configuration schematic diagram that the utility model is tested for wheel disc;
Fig. 2 is the A-A cut-open view of Fig. 1;
Fig. 3 is the structural representation of balancing weight;
Fig. 4 is the structural representation of compensating groove;
Wherein, 1-balancing weight; 2-wheel disc; 3-compensating groove; 4-balancing bolt mounting hole.
Embodiment
Below by concrete embodiment, the utility model is described in further detail: please refer to Fig. 1, Fig. 2, Fig. 3, wherein, Fig. 1 is the wheel rim centrifugal load model configuration schematic diagram that the utility model is tested for wheel disc, Fig. 2 is the A-A cut-open view of Fig. 1, Fig. 3 is the structural representation of balancing weight, and Fig. 4 is the structural representation of compensating groove.The wheel rim centrifugal load model configuration that the utility model is used for wheel disc test is made up of balancing weight 1 and wheel disc 2, and balancing weight 1 and wheel disc 2 are that overall processing is shaping, and wherein, wheel disc body structure is consistent with the structure of the true wheel disc of engine.
Described balancing weight is along the thickness L of wheel disc axis
1with true rim axle to consistency of thickness, balancing weight bottom radius R
1consistent with bottom true wheel disc chase mortise; The tip radlus of true wheel disc is R
2, blade quantity is n
1.Balancing weight is circumferential partitioned organization, and quantity is n
2, single balancing weight angle is circumferentially 360 °/n
2, the distance of the peripheral boundaries of balancing weight and its cut-off rule is L
2, the peripheral boundaries distance between adjacent two balancing weights is 2L
2, the radial height of balancing weight is H
1.The utility model utilizes centrifugal force equivalence principle, by adjusting the radial height H of balancing weight
1change balancing weight quality and barycenter Deng structural parameters, and adjust balancing weight quantity n according to the centrifugal force of single balancing weight and the total centrifugal force demand of wheel disc outer rim
2, the stress distribution on adjustment wheel disc, to realize the centrifugal force of simulating the real structure such as blade and tongue and groove couplijng with balancing weight shown in Fig. 2.
In order to reduce the stress level of balancing weight root, being designed with compensating groove two ends shown in compensating groove 3, Fig. 3 at balancing weight root is radius R
3circular arc, circular arc end points to balancing weight peripheral boundaries distance be L
3, compensating groove is highly radially 2R
3, circumferentially length is 2 (L
2+ L
3+ R
3).For compensating groove arc radius R
3adjustment, with its stress parameters be less than the wheel disc life-span examination point be as the criterion, also by adjustment radius R
3realize the simulation to tongue-and-groove stress; And adjacent two compensating groove spacing L
4then to ensure that necking down cross-sectional strength is as the criterion.For the structural parameters of balancing weight, wherein L
2span be 1 ~ 1.5mm, H
1span be no more than R
2-(R
1+ 2R
3), quantity n
2be no more than number of blade n
1.
Eccentric throw can be produced when the center of gravity of wheel disc testpieces and center of rotation do not overlap, wheel disc testpieces is made to occur large vibration when High Rotation Speed, therefore, balancing weight is designed with balancing bolt mounting hole 4 along the thickness direction of wheel disc axis, its objective is the balancing bolt that can install appropriate mass herein additional, make it close to center of rotation to reduce amount of unbalance with the center of gravity adjusting wheel disc testpieces, reduce level of vibration.The radius of balancing bolt mounting hole 4 is R
4, each balancing weight center line arranges one, is 180 °/n with the angle of balancing weight cut-off rule
2, radius R
4span is 2.5 ~ 3.0mm, and balancing bolt mounting hole 4 can be radial at (R along wheel disc
1+ 2R
3) ~ (R
1+ 2R
3+ H
1) scope moves.The utility model by arranging balancing weight on wheel disc, and the position to balancing weight, structural parameters etc. design consideration in many ways, realize the effective simulation to wheel disc centrifugal force, and significantly reduce experimentation cost.And by arranging balancing bolt mounting hole on balancing weight, effectively reduce vibration, improve test simulation effect, there is larger economic benefit.
Claims (7)
1., for a wheel rim centrifugal load model configuration for wheel disc test, it is characterized in that, comprise balancing weight and wheel disc, wherein, described balancing weight is circumferential partitioned organization, is arranged on wheel disc outer rim, and quantity is n
2, single balancing weight angle is circumferentially 360 °/n
2, described balancing weight is along the thickness L of wheel disc axis
1with true rim axle to consistency of thickness, balancing weight bottom radius R
1consistent with bottom true wheel disc chase mortise.
2. the wheel rim centrifugal load model configuration for wheel disc test according to claim 1, it is characterized in that, the distance of the peripheral boundaries of balancing weight and its cut-off rule is L
2, the peripheral boundaries distance between adjacent two balancing weights is 2L
2.
3. the wheel rim centrifugal load model configuration for wheel disc test according to claim 2, is characterized in that, described L
2span be 1 ~ 1.5mm, the span of the radial height H1 of balancing weight is no more than R
2-(R
1+ 2R
3), wherein, n
2be no more than number of blade n
1, R
2for the tip radlus of wheel disc, R
3for compensating groove arc radius.
4. the wheel rim centrifugal load model configuration for wheel disc test according to claim 3, it is characterized in that, described balancing weight root is provided with compensating groove.
5. the wheel rim centrifugal load model configuration for wheel disc test according to claim 4, it is characterized in that, described balancing weight is designed with balancing bolt mounting hole along the thickness direction of wheel disc axis.
6. the wheel rim centrifugal load model configuration for wheel disc test according to claim 5, it is characterized in that, the radius of balancing bolt mounting hole is R
4, each balancing weight center line arranges one, is 180 °/n with the angle of balancing weight cut-off rule
2, radius R
4span is 2.5 ~ 3.0mm.
7. the wheel rim centrifugal load model configuration for wheel disc test according to claim 6, it is characterized in that, balancing bolt mounting hole is (R along the mobile space of wheel disc radial direction
1+ 2R
3) ~ (R
1+ 2R
3+ H
1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420706154.8U CN204255625U (en) | 2014-11-20 | 2014-11-20 | A kind of wheel rim centrifugal load model configuration for wheel disc test |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420706154.8U CN204255625U (en) | 2014-11-20 | 2014-11-20 | A kind of wheel rim centrifugal load model configuration for wheel disc test |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204255625U true CN204255625U (en) | 2015-04-08 |
Family
ID=52959920
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420706154.8U Active CN204255625U (en) | 2014-11-20 | 2014-11-20 | A kind of wheel rim centrifugal load model configuration for wheel disc test |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204255625U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107314893A (en) * | 2017-05-08 | 2017-11-03 | 上海交通大学 | A kind of modular multi-function rotor testbed |
| CN114034587A (en) * | 2021-11-10 | 2022-02-11 | 中国航发湖南动力机械研究所 | Simulation disc for low-cycle fatigue test of turbine working blade |
| CN115266061A (en) * | 2022-07-27 | 2022-11-01 | 中国航发沈阳发动机研究所 | Low cycle fatigue life simulation piece of fan dish tongue-and-groove |
-
2014
- 2014-11-20 CN CN201420706154.8U patent/CN204255625U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107314893A (en) * | 2017-05-08 | 2017-11-03 | 上海交通大学 | A kind of modular multi-function rotor testbed |
| CN114034587A (en) * | 2021-11-10 | 2022-02-11 | 中国航发湖南动力机械研究所 | Simulation disc for low-cycle fatigue test of turbine working blade |
| CN115266061A (en) * | 2022-07-27 | 2022-11-01 | 中国航发沈阳发动机研究所 | Low cycle fatigue life simulation piece of fan dish tongue-and-groove |
| CN115266061B (en) * | 2022-07-27 | 2023-08-04 | 中国航发沈阳发动机研究所 | Low cycle fatigue life simulation piece of fan disc mortise |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN204255625U (en) | A kind of wheel rim centrifugal load model configuration for wheel disc test | |
| CN204183185U (en) | A kind of device turning stator part assembling for aero-engine and measure | |
| CN103994856B (en) | A kind of high speed rotor dynamic response test platform calibration standard rotor | |
| CN203809628U (en) | Round sliding block, round sliding block set, internal-combustion engine, compressor and plunger pump | |
| CN207500044U (en) | A kind of device positioned for wind power generation unit blade with installing | |
| CN103452914A (en) | Assembly technique for reducing dynamic balance of rotor of turbocharger | |
| CN107389364A (en) | A kind of inertia load weighted platform | |
| CN203522424U (en) | Balance ring of motor | |
| CN104330317A (en) | High-temperature and high-cycle compound fatigue test platform for turbine blade | |
| CN105003635A (en) | Supporting device for gearbox, installation method and maintenance method | |
| CN106017795B (en) | compressor rotor balancing fixture | |
| CN207600752U (en) | For turboshaft engine birotor experimental bench can dissection type support construction | |
| CN204140599U (en) | Split shaft block ring | |
| CN203685972U (en) | Two-stage damping structure for table centrifuge | |
| CN102852849B (en) | Coupler for eliminating balance clearance of fan rotor | |
| CN106768768B (en) | A kind of angle of continuously adjustabe misaligns rotor fault simulation mechanism | |
| CN204784614U (en) | Support arrangement for be used for gear box | |
| CN202471352U (en) | Equivalent ring for engine crankshaft dynamic balance test | |
| CN204255548U (en) | The flywheel tunable arrangement of vehicle dynamic test machine | |
| CN204043914U (en) | For the flywheel gear of Aero-Engine Start test run | |
| CN203236553U (en) | Multi-saw-blade woodworking machine saw blade shaft eccentric gear adjusting mechanism | |
| CN208397189U (en) | A kind of high-precision dynamic vibration absorber | |
| WO2014053130A3 (en) | Torsional vibration damper | |
| CN104344930A (en) | Rotor head angle contact ball bearing variable-pitch propeller hub for helicopter blade dynamic balance test table | |
| CN204194262U (en) | Eccentric block component |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP03 | Change of name, title or address |
Address after: No. 999, Xuefu Road, Xindu, Chengdu, Sichuan 610500 Patentee after: AECC SICHUAN GAS TURBINE Research Institute Address before: 621703 operation monitoring department, mailbox 305, Jiangyou, Sichuan, Mianyang, Sichuan Patentee before: CHINA GAS TURBINE EST |
|
| CP03 | Change of name, title or address |