CN104267617B - A kind of dynamic load simulation test experiment platform and method of testing - Google Patents
A kind of dynamic load simulation test experiment platform and method of testing Download PDFInfo
- Publication number
- CN104267617B CN104267617B CN201410510967.4A CN201410510967A CN104267617B CN 104267617 B CN104267617 B CN 104267617B CN 201410510967 A CN201410510967 A CN 201410510967A CN 104267617 B CN104267617 B CN 104267617B
- Authority
- CN
- China
- Prior art keywords
- flywheel
- dynamic
- load
- slide unit
- torque
- 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.)
- Expired - Fee Related
Links
Landscapes
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
- Force Measurement Appropriate To Specific Purposes (AREA)
Abstract
The invention discloses a kind of dynamic load simulation test experiment platform, one end of first torque sensor is connected to subjects by the first shaft coupling, the other end is connected with one end of described axle by the second shaft coupling, the other end of axle is connected with one end of described second torque sensor by the 3rd shaft coupling, and the other end of the second torque sensor is connected to described magnetic powder brake；Clutch shaft bearing, angular transducer, slip ring, flywheel, clutch and the second bearing are sequentially set with on the shaft；Multiple electric linear slide unit is installed on flywheel wheel face equably.Inertia load suffered by tested object, torque loads can be measured in process of the test by this platform in real time, and according to predetermined target automatic stepless regulation inertia load and torque loads, process of the test is by TT&C system closed loop control, therefore precision is high.Test platform flywheel disc structure intensity is high, good stability, and reliability is high.
Description
Technical field
The invention belongs to Experiments of Machanics technical field, specific design one dynamic load simulation test experiment platform and test
Method.
Background technology
Load simulation technology refers in laboratory conditions, by the carrying of certain technological means simulation loading object
Or moment, it is a kind of emerging HWIL simulation and experimental technique.In the research and test of new product and new technique, load mould
Plan technology overcomes and the loading object of reality must be used in actual environment to carry out the limitation studied, and is possible not only to save examination
Test cost, reduce empirical risk, and some research approaches that cannot realize in practice and system model can also be by half
Load simulation platform in kind realizes.Especially in such as Aero-Space, ocean engineering etc., some are difficult to carry out on-line testing
Field, load simulation technology just seems more important.
One general load simulation system typically requires can simulate inertia load and torque loads (includes that friction is negative
Load, constant value load, variable load etc.).Chinese patent Authorization Notice No. be 201220233572.0 patent disclose a kind of mould
Intending load experiment device, for testing motor and speed reducer, this fictitious load assay device includes driven gear, actively
Gear, speed increaser, flying wheel, tested motor and speed reducer, this invention can be simulated inertia load and torque loads simultaneously, but tried
Can not in real time and the load value that applied of step-less adjustment during testing.In the prior art in order to realize regulating in test inertia
Load, the general quantity using change Flywheel disc, change inertia load by dismounting Flywheel disc, therefore adjust inertia load every time
Operate the most loaded down with trivial details, in order to simplify adjustment process, prior art also has some optimize.Such as, Chinese patent Granted publication
Number be 201120176448.0 patent disclose a kind of rotary inertia adjusting means, this device include least one set joint arm,
Moving mass, motor and main shaft, realized rotary inertia the control of main shaft upper joint arm and moving mass by motor
Regulation.Although this device can realize the step-less adjustment of rotary inertia, but also exist in the case of high-speed rotation structural instability,
The problems such as joint arm easily snaps off.Chinese patent Authorization Notice No. be 201120198960.5 patent disclose a kind of moment of torsion and bear
Load simulator, the friction plate being contained in rotating shaft including rotating shaft and bearing holder (housing, cover), by manually tightening up the elastic component on the bar of location,
Changing friction plate and produce different torque loads from the frictional force of rotating shaft, this invention can not realize the real-time regulation of load, and
And along with the use of load simulator, friction plate can wear and tear.In the case of same tightening amount, torque loads can change,
Therefore load simulation precision is relatively low.
Summary of the invention
The deficiency existed in view of above-mentioned prior art, present invention aim to provide one can accurately simulate dynamically
Inertia load and dynamic torque load test platform and the method for testing of (including the load of friction load, constant value, variable load etc.).
Inertia load suffered by tested object, torque loads can be measured in process of the test by this platform in real time, and according in advance
Fixed target automatic stepless regulation inertia load and torque loads, process of the test is by TT&C system closed loop control, therefore precision is high.Examination
Testing platform flywheel disc structure intensity high, good stability, reliability is high.
In order to achieve the above object, the present invention is achieved by the following technical programs:
A kind of dynamic load simulation test experiment platform, including the first torque sensor, clutch shaft bearing, angular transducer,
Slip ring, flywheel, clutch, the second bearing, the second torque sensor, magnetic powder brake and TT&C system, described first moment of torsion passes
One end of sensor is connected to subjects by the first shaft coupling, and the other end is connected by one end of the second shaft coupling with described axle
Connecing, the other end of described axle is connected with one end of described second torque sensor by the 3rd shaft coupling, and described second moment of torsion passes
The other end of sensor is connected to described magnetic powder brake；
Described clutch shaft bearing, angular transducer, slip ring, flywheel, clutch and the second bearing are sequentially set with on the shaft；
Multiple electric linear slide unit is installed on described flywheel wheel face equably, every pair facing each other described electronic directly
Line slide unit is symmetrical about the revenue centre of flywheel；Described electric linear slide unit includes near the centrally disposed motor of flywheel, slide block
And balancing weight, described balancing weight is fixed on described slide block, and the sliding action of described slide block is driven by described motor；
Described TT&C system respectively with the first torque sensor, the second torque sensor, angular transducer and magnetic powders brake
Device is connected, and is connected by the motor of slip ring with electric linear slide unit.
Preferably, the mass centre of the plurality of electric linear slide unit and the center superposition of flywheel.
Preferably, the centre bore that described flywheel center is offered is built with the 3rd bearing, and described 3rd bearing holder (housing, cover) is at axle
On；Between described flywheel and clutch relative to end be respectively disposed with the tooth being meshed a pair；Locking it is disposed with on clutch
Screw, described axle has been sequentially arranged along direction away from described flywheel the first locking hole, the second locking hole and for spacing
Third gear circle；When described flywheel engages with clutch, described lock-screw aligns with described first locking hole；When described from
When clutch is resisted against on third gear circle, described flywheel and throw-out-of clutch, described lock-screw aligns with the second locking hole.
Preferably, balancing weight identical in quality installed about flywheel centrosymmetry.
Preferably, described electric linear slide unit is the electronic slide unit of ball-screw, and described motor is servomotor, and it drives rolling
Ballscrew rotates, and described ball-screw band movable slider moves.
Preferably, described flywheel also includes basal disc, and on described basal disc, the revenue centre about flywheel is offered porose symmetrically
Hole, to reduce the rotary inertia of described basal disc.
The wire of electric linear slide unit on described flywheel is connected with the slip ring on axle, it is ensured that motor on electric linear slide unit
Wire will not be intertwined when rotated.Slip ring is mounted on an axle.
Preferably, circle magnetic grid selected by described angular transducer.
Preferably, described first shaft coupling, the second shaft coupling and the 3rd shaft coupling, select single-iris shaft coupling.
Preferably, described bearing, bearing, select deep groove ball bearing.
Preferably, described 3rd Selection of Bearings needle bearing.
As a kind of improved procedure, according to actual needs, flywheel can be arranged that the even-even electric linears such as 2,4,6,8 are sliding
Platform.
As a kind of improved procedure, basal disc can use regular polygon steel plate or aluminium sheet, such as square, regular hexagon,
Octagon etc., centre can symmetrical hollow out to reduce the rotary inertia of basal disc.
As a kind of improved procedure, described balancing weight can change the balancing weight of different quality according to different tests.
The present invention can simulate simultaneously Dynamic Inertia load and dynamic torque load (include friction load, constant value load, can
Varying load etc.) multiple its load form, it is also possible to simulation any of which load.In simulation process, can real-time testing tested
The moment of torsion of object, corner, rotating speed and angular acceleration, and inertia load and torque loads are carried out real-time, regulate accurately, improve
Dynamic load simulation precision.
A kind of dynamic load analog detection method, comprises the following steps:
A () test system, according to the characteristic of measurand, sets up the function J=F of Dynamic Inertia load J t in timeJ(t)
And the function T=F of dynamic torque load T t in timeT(t), function can be equation form can also be parameter list form.
B () starts tested object, TT&C system constantly reads output valve T of the first torque sensor1, the second torque sensing
Output valve T of device2Output valve θ with angular transducer.The most at a time ti, torque loads T of magnetic powder brake generationi=
T2, the inertia load of flywheel generation
C () is by measured inertia load Ji, torque loads TiRelation function contrast with setting up in step (a), calculates
tiMoment inertia load deviation eJi=FJ(ti)-JiAnd torque loads deviation eTi=FT(ti)-Ti, then calculated by pid algorithm
Subsequent time electric linear slide unit and the output valve of magnetic powder brake, and control its action respectively.
D () inputs according to user, it may be judged whether stop experiment, if it is stops experiment, otherwise returns and perform step
(b)。
For said method, it is preferred that also can set up the Dynamic Inertia load J function J=F with rotational angle thetaJ(θ) and dynamically
Torque loads T is with the function T=F of rotational angle thetaT(θ)。
Accompanying drawing explanation
Fig. 1 is the schematic diagram of a kind of dynamic load simulation test experiment platform.
Fig. 2 is the schematic diagram of flywheel.
Fig. 3 is flywheel assembly partial enlarged drawing.
Fig. 4 is load simulation test method flow chart.
In figure, 1-subjects, 2-the first shaft coupling, 3-the first torque sensor, 4-the second shaft coupling, 5-the first axle
Hold, 6-angular transducer, 7-slip ring, 8-flywheel, 9-the 3rd bearing, 10-axle, 11-clutch 12-the second bearing, 13-the 3rd
Axial organ, 14-the second torque sensor, 15-magnetic powder brake, 16-TT&C system, 8-1-electric linear slide unit, 8-2-balancing weight,
8-3-basal disc, 17-end cap, 18-lock-screw, 19-the first back-up ring, 20-the second back-up ring, 21-third gear circle, 22-support.
Detailed description of the invention
Purpose and technical scheme for making the embodiment of the present invention are clearer, attached below in conjunction with the embodiment of the present invention
Figure, is clearly and completely described the technical scheme of the embodiment of the present invention.Obviously, described embodiment is the present invention
A part of embodiment rather than whole embodiments.Based on described embodiments of the invention, those of ordinary skill in the art
The every other embodiment obtained on the premise of without creative work, broadly falls into the scope of protection of the invention.
Those skilled in the art of the present technique are appreciated that unless otherwise defined, and all terms used herein (include technology art
Language and scientific terminology) have with the those of ordinary skill in art of the present invention be commonly understood by identical meaning.Also should
Being understood by, those terms defined in such as general dictionary should be understood that the meaning having with the context of prior art
The meaning that justice is consistent, and unless defined as here, will not explain by idealization or the most formal implication.
The implication of heretofore described "and/or" refers to respective individualism or both simultaneous situations are all wrapped
Including including.
The implication of heretofore described " inside and outside " refers to relative to equipment itself, the side within sensing equipment
To for interior, otherwise it is outward, rather than the specific restriction to assembly of the invention mechanism.
When the implication of heretofore described " left and right " refers to reader just to accompanying drawing, the left side of reader is a left side,
The right of reader is the right side, rather than the specific restriction to assembly of the invention mechanism.
The implication of heretofore described " connection " can be being directly connected between parts can also be to pass through between parts
Being indirectly connected with of other parts.
As it is shown in figure 1, the present invention provides a kind of dynamic load simulation test experiment platform, mainly by the first torque sensor
3, clutch shaft bearing 5, angular transducer 6, slip ring 7, flywheel 8, clutch the 11, second bearing the 12, second torque sensor 14, magnetic powder
Brake 15, TT&C system 16 form.It is right that one end of described first torque sensor 3 is connected to test by the first shaft coupling 2
As 1, the other end is connected with one end of described axle 10 by the second shaft coupling 4, and the other end of described axle 10 passes through the 3rd shaft coupling
13 are connected with one end of described second torque sensor 14, and the other end of described second torque sensor 14 is connected to described magnetic powder
Brake 15；Described clutch shaft bearing 5, angular transducer 6, slip ring 7, flywheel 8, clutch 11 and the second bearing 12 are sequentially sleeved on
On described axle 10；As in figure 2 it is shown, be provided with multiple electric linear slide unit 8-1 on described flywheel 8 wheel face equably, every pair mutually
The described electric linear slide unit 8-1 faced is symmetrical about the revenue centre of flywheel 8；Described electric linear slide unit 8-1 includes leaning on
Motor, slide block and the balancing weight 8-2 that nearly flywheel 8 is centrally disposed, described balancing weight 8-2 is fixed on described slide block, described slide block
Sliding action driven by described motor；Described TT&C system 16 respectively with first torque sensor the 3, second torque sensor
14, angular transducer 6 is connected with magnetic powder brake 15, is connected by the motor of slip ring 7 with electric linear slide unit 8-1.Described many
The mass centre of individual electric linear slide unit 8-1 and the center superposition of flywheel 8.
As it is shown on figure 3, the centre bore that described flywheel 8 center is offered is built with the 3rd bearing 9, described 3rd bearing 9
It is enclosed within axle 10；Between described flywheel 8 and clutch 11 relative to end be respectively disposed with the tooth being meshed a pair；Clutch 11
On be disposed with lock-screw 18, described axle 10 has been sequentially arranged along direction away from described flywheel 8 the first locking hole, second
Locking hole and for spacing third gear circle 21；When described flywheel 8 engages with clutch 11, described lock-screw 18 is with described
First locking hole alignment；When described clutch 11 is resisted against on third gear circle 21, described flywheel 8 disengages with clutch 11, institute
State lock-screw 18 to align with the second locking hole.Balancing weight identical in quality installed about flywheel 8 centrosymmetry.Described electronic
Straight line slide unit 8-1 is the electronic slide unit of ball-screw, and described motor is servomotor, and it drives ball-screw to rotate, described ball
Leading screw band movable slider moves.Described flywheel 8 also includes basal disc 8-3, and on described basal disc 8-3, the revenue centre about flywheel 8 is symmetrical
Offer hole, to reduce the rotary inertia of described basal disc 8-3.
Wire in order to ensure on electric linear slide unit 8-1 on motor will not be intertwined when rotated, and axle 10 is pacified
Dress slip ring 7, slip ring 7 spline sheet is fixed on support, and slip ring 7 flange is fixed on end cap 17.Wire connection slip ring 7 rotor limit,
When flywheel 8 rotates, stator outlet not concomitant rotation.
Concrete, in process of the test, TT&C system the 16, first torque sensor 3, angular transducer the 6, second moment of torsion pass
Sensor 14, magnetic powder brake 15, electric linear slide unit 8-1 constitute closed loop.
Refering to Fig. 4, it is the simulation drawing of load simulation test method of the present invention.Described load simulation test method is specifically wrapped
Include following steps:
Test system, according to the characteristic of measurand, sets up the function J=F of Dynamic Inertia load J t in timeJ(t) and dynamic
The function T=F of state torque loads T t in timeT(t), function can be equation form can also be parameter list form.
B () starts tested object 1, TT&C system constantly reads output valve T of the first torque sensor 31, second moment of torsion pass
Output valve T of sensor 142Output valve θ with angular transducer 6.The most at a time ti, the moment of torsion that magnetic powder brake 15 produces is born
Carry Ti=T2, inertia load that flywheel (8) produces
C () is by measured inertia load Ji, torque loads TiRelation function contrast with setting up in step (a), calculates
tiMoment inertia load deviation eJi=FJ(ti)-JiAnd torque loads deviation eTi=FT(ti)-Ti, then calculated by pid algorithm
The output valve of subsequent time electric linear slide unit 8-1, and control its action respectively.TiMoment electric linear slide unit 8-1's is defeated
Go out to be worth Δ FJi(ti) calculated by following formula:
ΔFJi(ti)=kJp(eJi-eJi-1)+kJIeJi+kJD(eJi-2eJi-1+eJi-2)
eJi、eJi-1、eJi-2: it is the t between Dynamic Inertia load input and setting value respectivelyiMoment, ti-1Moment,
ti-2Instance sample deviation value；
kJP: the proportionality coefficient of Dynamic Inertia load；
kJI: the integral coefficient of Dynamic Inertia load；
kJD: the differential coefficient of Dynamic Inertia load.
T is calculated by pid algorithmiThe output valve of moment magnetic powder brake 15, and control its action.TiMoment magnetic powder system
Output valve F of dynamic device 15Ti(ti) calculated by following formula:
FTi(ti)=FTi-1(ti-1)+kTp(eTi-eTi-1)+kTIeTi+kTD(eTi-2eTi-1+eTi-2)
FTi(ti): magnetic powder brake tiThe output valve in moment.
FTi-1(ti-1): magnetic powder brake ti-1The output valve in moment.
eTi、eTi-1、eTi-2: it is the t between dynamic torque load input and setting value respectivelyiMoment, ti-1Moment,
ti-2Instance sample deviation value.
kTP: the proportionality coefficient of dynamic torque load.
kTI: the integral coefficient of dynamic torque load.
kTD: the differential coefficient of dynamic torque load.
D () inputs according to user, it may be judged whether stop experiment, if it is stops experiment, otherwise returns and perform step
(b)。
As another embodiment of load simulation test method, as follows:
A () also can set up the Dynamic Inertia load J function J=F with rotational angle thetaJ(θ) and dynamic torque load T with rotational angle theta
Function T=FT(θ)。
B () starts tested object 1, TT&C system constantly reads output valve T of the first torque sensor 31, second moment of torsion pass
Output valve T of sensor 142Output valve θ with angular transducer 6.Then in a certain rotational angle thetai, the moment of torsion that magnetic powder brake 15 produces is born
Carry Ti=T2, the inertia load of flywheel 8 generation
C () is by measured inertia load Ji, torque loads TiRelation function contrast with setting up in step (a), calculates
θiInertia load deviation e during cornerJi=FJ(θi)-JiAnd torque loads deviation eTi=FT(θi)-Ti, then by pid algorithm meter
Electric linear slide unit 8-1 and the output valve of magnetic powder brake 15 when calculating next corner, and control its action respectively.θiDuring corner
The output valve Δ F of electric linear slide unit 8-1Ji(θi) calculated by following formula:
ΔFJi(θi)=kJp(eJi-eJi-1)+kJIeJi+kJD(eJi-2eJi-1+eJi-2)
eJi、eJi-1、eJi-2: it is the θ between Dynamic Inertia load input and setting value respectivelyiCorner, θi-1Corner,
θi-2Corner sampling deviation value.
kJP: the proportionality coefficient of Dynamic Inertia load.
kJI: the integral coefficient of Dynamic Inertia load.
kJD: the differential coefficient of Dynamic Inertia load.
θ is calculated by pid algorithmiThe output valve of corner magnetic powder brake 15, and control its action.θiCorner magnetic powder system
Output valve F of dynamic device 15Ti(θi) calculated by following formula:
FTi(θi)=FTi-1(θi-1)+kTp(eTi-eTi-1)+kTIeTi+kTD(eTi-2eTi-1+eTi-2)
FTi(θi): dynamic torque load θiOutput valve during corner.
FTi-1(θi-1): dynamic torque load θi-1Output valve during corner.
eTi、eTi-1、eTi-2: it is the θ between dynamic torque load input and setting value respectivelyiCorner, θi-1Corner,
θi-2Corner sampling deviation value.
kTP: the proportionality coefficient of dynamic torque load.
kTI: the integral coefficient of dynamic torque load.
kTD: the differential coefficient of dynamic torque load.
D () inputs according to user, it may be judged whether stop experiment, if it is stops experiment, otherwise returns and perform step
(b)。
When in the present embodiment, clutch 11 between axle 10 with flywheel 8 separates, flywheel 8 does not rotates with axle 10.Now move
State load simulation test experiments platform only applies torque loads to tested object 1.
In the present embodiment, the clutch 11 between axle 10 with flywheel 8 engages, and regulates magnetic powder brake 15 braking moment
Being zero, now dynamic load simulation test platform only applies inertia load to tested object 1.
These are only embodiments of the present invention, it describes more concrete and in detail, but can not therefore and be interpreted as right
The restriction of the scope of the claims of the present invention.It should be pointed out that, for the person of ordinary skill of the art, without departing from the present invention
On the premise of design, it is also possible to make some deformation and improvement, these belong to protection scope of the present invention.
Claims (8)
1. a dynamic load simulation test experiment platform, including the first torque sensor (3), clutch shaft bearing (5), angle sensor
Device (6), slip ring (7), flywheel (8), clutch (11), the second bearing (12), the second torque sensor (14), magnetic powder brake
(15) and TT&C system (16), it is characterised in that one end of described first torque sensor (3) is by the first shaft coupling (2) even
Being connected to subjects (1), the other end is connected with one end of axle (10) by the second shaft coupling (4), the other end of described axle (10)
It is connected by one end of the 3rd shaft coupling (13) with described second torque sensor (14), described second torque sensor (14)
The other end is connected to described magnetic powder brake (15)；
Described clutch shaft bearing (5), angular transducer (6), slip ring (7), flywheel (8), clutch (11) and the second bearing (12) are suitable
Secondary it is sleeved on described axle (10)；
Multiple electric linear slide unit (8-1) is installed equably, every pair of described electricity facing each other on described flywheel (8) wheel face
Dynamic straight line slide unit (8-1) is symmetrical about the revenue centre of flywheel (8)；Described electric linear slide unit (8-1) includes near flywheel (8)
Centrally disposed motor, slide block and balancing weight (8-2), described balancing weight (8-2) is fixed on described slide block, the cunning of described slide block
Dynamic action is driven by described motor；
Described TT&C system (16) respectively with the first torque sensor (3), the second torque sensor (14), angular transducer (6)
It is connected with magnetic powder brake (15), is connected by the motor of slip ring (7) with electric linear slide unit (8-1).
A kind of dynamic load simulation test experiment platform the most according to claim 1, it is characterised in that the plurality of electronic
The mass centre of straight line slide unit (8-1) and the center superposition of flywheel (8).
A kind of dynamic load simulation test experiment platform the most according to claim 2, it is characterised in that described flywheel (8)
The centre bore that center is offered is enclosed within axle (10) built with the 3rd bearing (9), described 3rd bearing (9)；Described flywheel (8)
And between clutch (11) relative to end be respectively disposed with the tooth being meshed a pair；Clutch is disposed with lock-screw on (11)
(18), described axle (10) is upper has been sequentially arranged the first locking hole, the second locking hole and use along the direction away from described flywheel (8)
In spacing third gear circle (21)；When described flywheel (8) engages with clutch (11), described lock-screw (18) and described the
One locking hole alignment；When described clutch (11) is resisted against on third gear circle (21), described flywheel (8) takes off with clutch (11)
Opening, described lock-screw (18) aligns with the second locking hole.
A kind of dynamic load simulation test experiment platform the most according to claim 2, it is characterised in that described flywheel (8)
Balancing weight identical in quality that centrosymmetry is installed.
A kind of dynamic load simulation test experiment platform the most according to claim 1, it is characterised in that described electric linear
Slide unit (8-1) is the electronic slide unit of ball-screw, and described motor is servomotor, and it drives ball-screw to rotate, described ball wire
Thick stick band movable slider moves.
A kind of dynamic load simulation test experiment platform the most according to claim 1, it is characterised in that described flywheel (8)
Also including basal disc (8-3), on described basal disc (8-3), flywheel (8) symmetrically offers hole, to reduce described basal disc
(8-3) rotary inertia.
7. one kind uses the dynamic load simulation test that dynamic load simulation test experiment platform as claimed in claim 1 is carried out
Method, it is characterised in that comprise the following steps:
A (), TT&C system (16), according to the characteristic of measurand (1), set up the function J=F of Dynamic Inertia load J t in timeJ
The function T=F of (t) and dynamic torque load T t in timeTT (), function uses equation form or parameter list form；
B (), startup tested object (1), TT&C system (16) constantly reads output valve T of the first torque sensor (3)1, second turn round
Output valve T of square sensor (14)2Output valve θ with angular transducer (6)；Then at moment ti, magnetic powder brake (15) produces
Torque loads Ti=T2, inertia load that flywheel (8) produces
(c), by measured inertia load Ji, torque loads TiRelation function contrast with setting up in step (a), calculates ti
Moment inertia load deviation eJi=FJ(ti)-JiAnd torque loads deviation eTi=FT(ti)-Ti, then calculated down by pid algorithm
One moment electric linear slide unit (8-1) and the output valve of magnetic powder brake (15), and respectively control electric linear slide unit (8-1) and
The action of magnetic powder brake (15)；
(d), according to user input, it may be judged whether stop experiment, if it is stop experiment, otherwise return perform step (b).
8. one kind uses the dynamic load simulation test that dynamic load simulation test experiment platform as claimed in claim 1 is carried out
Method, it is characterised in that comprise the following steps:
A (), TT&C system (16), according to the characteristic of measurand (1), set up the Dynamic Inertia load J function J=F with rotational angle thetaJ
(θ) and dynamic torque load T is with the function T=F of rotational angle thetaT(θ)；
B (), startup tested object (1), TT&C system constantly reads output valve T of the first torque sensor (3)1, second moment of torsion pass
Output valve T of sensor (14)2Output valve θ with angular transducer 6；Then in rotational angle thetai, the moment of torsion that magnetic powder brake (15) produces is born
Carry Ti=T2, the inertia load of flywheel 8 generation
(c), by measured inertia load Ji, torque loads TiRelation function contrast with setting up in step (a), calculates θi
Time inertia load deviation eJi=FJ(θi)-JiAnd torque loads deviation eTi=FT(θi)-Ti, then calculate next by pid algorithm
Corner electric linear slide unit (8-1) and the output valve of magnetic powder brake (15), and control electric linear slide unit (8-1) and magnetic respectively
The action of powder brake (15)；
(d), according to user input, it may be judged whether stop experiment, if it is stop experiment, otherwise return perform step (b).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410510967.4A CN104267617B (en) | 2014-09-28 | 2014-09-28 | A kind of dynamic load simulation test experiment platform and method of testing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410510967.4A CN104267617B (en) | 2014-09-28 | 2014-09-28 | A kind of dynamic load simulation test experiment platform and method of testing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104267617A CN104267617A (en) | 2015-01-07 |
| CN104267617B true CN104267617B (en) | 2016-10-26 |
Family
ID=52159145
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410510967.4A Expired - Fee Related CN104267617B (en) | 2014-09-28 | 2014-09-28 | A kind of dynamic load simulation test experiment platform and method of testing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104267617B (en) |
Families Citing this family (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104635157B (en) * | 2015-01-20 | 2017-06-30 | 山东拓博节能科技有限公司 | A kind of low rotation speed large torque electromechanical testing platform |
| CN104614188A (en) * | 2015-01-27 | 2015-05-13 | 武进高新技术创业服务中心 | Dynamic load simulator stand based on computer aided engineering (CAE) analysis |
| CN104849161A (en) * | 2015-04-29 | 2015-08-19 | 西安顺通机电应用技术研究所 | Automatic inertial flywheel disengaging-engaging mechanism for testbed |
| CN106248382B (en) * | 2015-06-15 | 2018-11-27 | 北京富华惠航航空科技有限公司 | Starter testing stand |
| CN105092236B (en) * | 2015-09-10 | 2017-12-22 | 中国铁路总公司 | A kind of device and method for testing eddy current damper damping due to rotation coefficient |
| CN106646220A (en) * | 2015-10-30 | 2017-05-10 | 北京精密机电控制设备研究所 | Spaceflight servo motor variable working condition dynamic loading system and spaceflight servo motor variable working condition dynamic loading method |
| CN106646219A (en) * | 2015-10-30 | 2017-05-10 | 北京精密机电控制设备研究所 | Inertia load simulation apparatus |
| CN105403397A (en) * | 2015-12-18 | 2016-03-16 | 海安县申菱电器制造有限公司 | Electromagnetic brake detection apparatus capable of simulating multiple loads |
| CN106125675A (en) * | 2016-08-04 | 2016-11-16 | 上海宇航系统工程研究所 | A kind of single shaft high-precision servo control system device for adjusting and measuring |
| CN107525663B (en) * | 2017-09-18 | 2020-02-21 | 江苏科技大学 | Dynamic load simulation test device and test method |
| CN108061652A (en) * | 2018-02-05 | 2018-05-22 | 重庆机床(集团)有限责任公司 | Gear hobbing machine worktable test platform and its test method |
| CN108132147A (en) * | 2018-03-14 | 2018-06-08 | 吉林大学 | A kind of electrical analogue compensation method of automobile clutch testing stand and Rotary Inertia of Flywheel |
| CN109188276A (en) * | 2018-09-06 | 2019-01-11 | 南京越博电驱动系统有限公司 | A kind of servo motor is to dragging platform |
| CN110696044B (en) * | 2019-10-28 | 2024-06-04 | 浙江工业大学 | Experimental device for simulating dynamic variable load and variable inertia of industrial robot joint |
| CN110696048B (en) * | 2019-10-28 | 2024-06-04 | 浙江工业大学 | Experimental device for simulating single-joint variable inertia variable load of industrial robot |
| CN110696045B (en) * | 2019-10-28 | 2024-06-04 | 浙江工业大学 | Experimental device for simulating variable load and variable inertia of industrial robot joint |
| CN110782768A (en) * | 2019-11-05 | 2020-02-11 | 西南交通大学 | Motor car traction braking experiment model device |
| CN111077450B (en) * | 2020-01-18 | 2024-06-07 | 贵州凯敏博机电科技有限公司 | Variable load device for motor test |
| CN212872795U (en) * | 2020-07-30 | 2021-04-02 | 上海拓攻机器人有限公司 | Load inertia simulation disc and motor testing device |
| CN113532855B (en) * | 2021-07-23 | 2024-03-12 | 北京卫星环境工程研究所 | Ground comprehensive test system for verifying joint life of aerospace mechanical arm |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5133211A (en) * | 1991-02-07 | 1992-07-28 | Aircraft Braking Systems Corporation | Wheel bearing test system |
| US7080565B2 (en) * | 2004-09-29 | 2006-07-25 | Raytheon Company | Dynamic load fixture for rotary mechanical systems |
| CN2914104Y (en) * | 2006-05-22 | 2007-06-20 | 比亚迪股份有限公司 | Testing device of electric motor |
| CN201110888Y (en) * | 2007-12-14 | 2008-09-03 | 大庆供电电器设备有限公司 | Self-starting rare-earth permanent magnet rotor type electric motor microcomputer integrated test apparatus |
| CN201255660Y (en) * | 2008-09-03 | 2009-06-10 | 中国船舶重工集团公司第七○四研究所 | Composite alternating torque and twist vibration loading experiment platform |
| DE102009026943B3 (en) * | 2009-06-15 | 2010-12-02 | Sven Henze | Bearing test device for testing of bearing units designed for bearing of rotor of wind power plant or shaft standing in drive connection with rotor, has torsional vibration chain, which is excited by drive unit and excitation unit |
| CN102539174A (en) * | 2011-12-26 | 2012-07-04 | 湘潭电机股份有限公司 | Load testing apparatus |
| CN103630319A (en) * | 2013-10-24 | 2014-03-12 | 浙江大学 | Impact test table based on axial loading of wind power high-speed shaft bearing |
-
2014
- 2014-09-28 CN CN201410510967.4A patent/CN104267617B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5133211A (en) * | 1991-02-07 | 1992-07-28 | Aircraft Braking Systems Corporation | Wheel bearing test system |
| US7080565B2 (en) * | 2004-09-29 | 2006-07-25 | Raytheon Company | Dynamic load fixture for rotary mechanical systems |
| CN2914104Y (en) * | 2006-05-22 | 2007-06-20 | 比亚迪股份有限公司 | Testing device of electric motor |
| CN201110888Y (en) * | 2007-12-14 | 2008-09-03 | 大庆供电电器设备有限公司 | Self-starting rare-earth permanent magnet rotor type electric motor microcomputer integrated test apparatus |
| CN201255660Y (en) * | 2008-09-03 | 2009-06-10 | 中国船舶重工集团公司第七○四研究所 | Composite alternating torque and twist vibration loading experiment platform |
| DE102009026943B3 (en) * | 2009-06-15 | 2010-12-02 | Sven Henze | Bearing test device for testing of bearing units designed for bearing of rotor of wind power plant or shaft standing in drive connection with rotor, has torsional vibration chain, which is excited by drive unit and excitation unit |
| CN102539174A (en) * | 2011-12-26 | 2012-07-04 | 湘潭电机股份有限公司 | Load testing apparatus |
| CN103630319A (en) * | 2013-10-24 | 2014-03-12 | 浙江大学 | Impact test table based on axial loading of wind power high-speed shaft bearing |
Non-Patent Citations (1)
| Title |
|---|
| 面向混合驱动实验平台加载的磁粉制动器磁滞特性研究;穆安乐 等;《西安理工大学学报》;20081231;第24卷(第1期);第58-61页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104267617A (en) | 2015-01-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104267617B (en) | A kind of dynamic load simulation test experiment platform and method of testing | |
| Zhou et al. | Correlation between preload and no-load drag torque of ball screws | |
| EP1746399A1 (en) | Estimating torque/force exerted by a load against a motor-driven actuator | |
| CN104006966B (en) | Geared rotor system vibration and gear housing are vibrated experimental provision and the verification method of the affecting laws that intercouples by load | |
| CN102419291B (en) | Rolling friction-wear testing machine capable of controlling friction coefficient and slip frequency on line | |
| Vasudevan et al. | Design for control of wheeled inverted pendulum platforms | |
| Olaru et al. | New micro tribometer for rolling friction | |
| US9632007B2 (en) | Method for damping vibrations while testing a drivetrain having at least one shaft | |
| CN108132147A (en) | A kind of electrical analogue compensation method of automobile clutch testing stand and Rotary Inertia of Flywheel | |
| EP2673610B1 (en) | Method and device for simulating a body that is moved in a translational or rotational manner | |
| CN109871044A (en) | A kind of rotating-speed tracking method and device | |
| CN103335832B (en) | Electric inertia simulation Ventilation disk brake testing stand and electric inertia simulation control method | |
| CN103344424B (en) | Ventilation disk brake electric inertia simulation testing stand and electric inertia simulation control method thereof | |
| Alyshev et al. | Parametric identification of reaction wheel pendulums with adaptive control | |
| Tong et al. | Harmonic gear reducer transmission error analysis and detection | |
| CN109145501A (en) | A kind of aero-engine intershaft bearing local damage fault vibration emulation mode | |
| KR20180014827A (en) | Test Bench for Charging Device | |
| Brzakovic et al. | A method for determination of kinetic friction coefficient under dynamic loading conditions | |
| Sundar et al. | Estimation of coefficient of friction for a mechanical system with combined rolling–sliding contact using vibration measurements | |
| Mozzhechkov et al. | Industrial valves with electric actuators: Technical diagnostics by a moment sensor within smart actuator worm-and-wheel gearbox | |
| Zheng et al. | Research on analysis method of dynamic friction torque of high speed precision miniature bearings | |
| Strelnikov et al. | Experimental investigation on interaction of wave disk generator with flexible gear | |
| US8447531B2 (en) | Device for measuring retention force | |
| Malafeev et al. | Mechatronic simulation of the 300 rolling mill | |
| Castilla et al. | Experimental study of the shaft motion in the journal bearing of a gear pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20161026 Termination date: 20190928 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |