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 PDF

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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
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China
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wheel
wheel disc
counterweight
rim
centrifugal load
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CN201420706154.8U
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Chinese (zh)
Inventor
潘容
冯引利
杨勋
何云
龚梦贤
孙海鹤
刘红彬
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AECC Sichuan Gas Turbine Research Institute
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China Gas Turbine Research Institute
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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

A kind of wheel rim centrifugal load model configuration for wheel disc test
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)

1.一种用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，包括配重块和轮盘，其中，所述配重块为周向分块结构，设置在轮盘外缘，数量为n2，单个配重块沿周向的角度为360°/n2，所述配重块沿轮盘轴向的厚度L1与真实轮缘轴向厚度一致，配重块底部半径R1与真实轮盘榫槽底部一致。1. A rim centrifugal load simulation structure for wheel disk test is characterized in that, comprises counterweight and wheel disc, wherein, said counterweight is a circumferential block structure, is arranged on wheel disc outer edge, The number is n 2 , the angle of a single counterweight along the circumferential direction is 360°/n 2 , the thickness L 1 of the counterweight along the axial direction of the wheel disc is consistent with the axial thickness of the real rim, and the radius R of the bottom of the counterweight is 1 Consistent with the real roulette tongue and groove bottom. 2.根据权利要求1所述的用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，配重块的周向边界与其分割线的距离为L2，相邻两个配重块之间的周向边界距离为2L2。2. The wheel rim centrifugal load simulation structure for roulette test according to claim 1, characterized in that the distance between the circumferential boundary of the counterweight and its dividing line is L 2 , and the distance between two adjacent counterweights is The circumferential boundary distance between them is 2L 2 . 3.根据权利要求2所述的用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，所述L2的取值范围为1～1.5mm，配重块的径向高度H1的取值范围不超过R2-(R1+2R3)，其中，n2不超过叶片数n1，R2为轮盘的叶尖半径，R3为卸荷槽圆弧半径。3. the rim centrifugal load simulation structure that is used for wheel disk test according to claim 2, is characterized in that, the value scope of described L 2 is 1～1.5mm, the radial height H1 of counterweight block takes The value range does not exceed R 2 -(R 1 +2R 3 ), where n 2 does not exceed the number of blades n 1 , R 2 is the blade tip radius of the wheel disk, and R 3 is the arc radius of the unloading groove. 4.根据权利要求3所述的用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，所述配重块根部设置有卸荷槽。4 . The wheel rim centrifugal load simulation structure for wheel disk test according to claim 3 , wherein an unloading groove is arranged at the root of the counterweight. 5 . 5.根据权利要求4所述的用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，所述配重块沿轮盘轴线的厚度方向设计有平衡螺栓安装孔。5 . The wheel rim centrifugal load simulation structure for wheel test according to claim 4 , characterized in that, the balance weight is designed with balancing bolt mounting holes along the thickness direction of the wheel axis. 6 . 6.根据权利要求5所述的用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，平衡螺栓安装孔的半径为R4，每个配重块中线上设置一个，与配重块分割线的夹角为180°/n2，半径R4取值范围为2.5～3.0mm。6. The wheel rim centrifugal load simulation structure for wheel disc test according to claim 5, characterized in that, the radius of the balance bolt mounting hole is R 4 , one is set on the center line of each counterweight, and the counterweight The included angle of the dividing line is 180°/n 2 , and the radius R 4 ranges from 2.5 to 3.0 mm. 7.根据权利要求6所述的用于轮盘试验的轮缘离心载荷模拟结构，其特征在于，平衡螺栓安装孔沿轮盘径向的移动间隙为(R1+2R3)～(R1+2R3+H1)。7. The wheel rim centrifugal load simulation structure for wheel test according to claim 6, characterized in that the movement clearance of the balance bolt mounting hole along the radial direction of the wheel is (R 1 +2R 3 )～(R 1 +2R 3 +H 1 ).
CN201420706154.8U 2014-11-20 2014-11-20 A kind of wheel rim centrifugal load model configuration for wheel disc test Expired - Lifetime CN204255625U (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
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
CN114896715A (en) * 2022-03-31 2022-08-12 中国航发沈阳发动机研究所 Aero-engine wheel disc balancing weight design method based on multi-objective optimization
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

Cited By (5)

* Cited by examiner, † Cited by third party
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
CN114896715A (en) * 2022-03-31 2022-08-12 中国航发沈阳发动机研究所 Aero-engine wheel disc balancing weight design method based on multi-objective optimization
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

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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

CX01 Expiry of patent term
CX01 Expiry of patent term

Granted publication date: 20150408