CN110162874A - Configure oscillating heat pipe electric chief axis system and its thermal-structure coupled characteristics modeling method - Google Patents
Configure oscillating heat pipe electric chief axis system and its thermal-structure coupled characteristics modeling method Download PDFInfo
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Abstract
The invention discloses configuration oscillating heat pipe electric chief axis system and its thermal-structure coupled characteristics modeling methods, including main shaft, it is arranged inside the main shaft housing, fore bearing and rear bearing, realize the fixation of main shaft and main shaft housing, the main shaft is connect with rotor, to realize the rotation of the main shaft, oscillating heat pipe is arranged inside the main shaft, between the cooling jacket and the main shaft housing in setting, the cooling device connecting with one end of the main shaft housing.The present invention provides the electric chief axis systems with good heat exchange property of configuration oscillating heat pipe, its modeling method is with analysis of finite element method high speed electric principal shaft system thermal-structure coupled characteristic, advantage is to simulate the working condition of electric chief axis system, the Deterministic Finite meta-model by way of amendment heat source load and thermal boundary condition, reduce the high-speed spindle system thermal-structure coupled characteristic modeling error configured with oscillating heat pipe, so that Finite element analysis results are closer to actual value.
Description
Technical field
The present invention relates to machinery fields, specifically, being related to configuring oscillating heat pipe electric chief axis system and its modeling method.
Background technique
Electro spindle is the new technology that machine tool chief axis and spindle motor combine together occurred in digit ctrol machine tool field.Main shaft
A set of component, it includes electro spindle itself and its attachment: electro spindle, high frequency converter plant, oil mist lubricator, cooling device,
Built-in encoder, tool changing device etc..The drive mechanism form of this spindle drive motor and machine tool chief axis " being combined into one ", makes main shaft
Component is relatively independent from the transmission system and overall structure of lathe to be come out, therefore can be made into " main axle unit ", is commonly called as " electricity master
Axis ", characteristic is high revolving speed, the structure of high-precision, low noise, inner wrap strip fore shaft is more suitable for oil foglubrication.But adding in lathe
During work, such as rolling bearing frictional heat generation etc., many factors can cause feed system thermo parameters method unevenness to generate thermal change
Shape and then influence numerically-controlled machine tool machining accuracy.The part life of electro spindle is influenced by temperature and thermal walking, still, is not had so far
There is method to be studied for the fining modeling of the temperature of electric chief axis system and thermal walking variation, it is even more impossible to electric mainshaft bearing
The service life of equal components makes a prediction.
Summary of the invention
In view of this, an object of the present invention is to provide configuration oscillating heat pipe electric chief axis system, advantage is main in electricity
It is provided with oscillating heat pipe in axis, there is good heat exchange property, the second purpose provides electric chief axis system thermal-structure coupled characteristic
Modeling method, with analysis of finite element method electric chief axis system thermal-structure coupled characteristic, advantage is to simulate electro spindle system
The working condition of system guarantees the modeling accuracy of finite element model by way of amendment heat source load and thermal boundary condition, reduces
Electric chief axis system thermal-structure coupled characteristic error, so that Finite element analysis results are closer to actual value.
The purpose of the present invention is what is be achieved through the following technical solutions:
Oscillating heat pipe electric chief axis system, including main shaft housing, encoder, motor stator, rotor are configured, further includes,
Main shaft is arranged inside the main shaft housing,
Fore bearing and rear bearing realize the fixation of main shaft and main shaft housing,
The main shaft is connect with rotor, to realize the rotation of the main shaft,
Cooling jacket is arranged in the motor stator outer surface；
Oscillating heat pipe is arranged inside the main shaft, between the cooling jacket and the main shaft housing in setting,
The cooling device being connect with one end of the main shaft housing,
The cooling device includes throttle valve, compressor, air pump and the cavity for being closed and being connected by pipeline, the air pump
Pipeline between cavity is set in cooling bath,
The oscillating heat pipe protrudes into the inside cavity relative to the main shaft housing extension end,
Cooling gas is arranged in the inside cavity.
A kind of electric chief axis system thermal-structure coupled characteristics modeling method, the modeling method specifically:
Step 1: establishing the high speed electric principal shaft system model for being configured with oscillating heat pipe；
Step 2: calculating and apply heat source load and thermal boundary condition in a model；
Step 3: obtaining characteristic point temperature value；
Step 4: determine whether to meet the condition of convergence,
Step 5: if convergence, draws temperature variation curve, terminating；If not restraining, step 6 is carried out；
Step 6: amendment heat source load and thermal boundary condition, return step 3.
Further, the heat source load includes motor heat amount, Rolling Components heat amount and variation of ambient temperature amount.
Further, the thermal boundary condition includes the coefficient of heat transfer, thermal contact resistance and the spindle unit and fluid of oscillating heat pipe
Between convection transfer rate, the thermal contact resistance includes the thermal contact resistance and bearing inner race and axle journal of bearing outer ring and bearing block
Thermal contact resistance.
Further, the decision condition are as follows:
Ti-Ti-10.05~0.15 DEG C of <
Ti: the temperature of characteristic point described in last moment；
Ti-1: the temperature of characteristic point described in this moment.
Further, the specific method for correcting the Rolling Components heat amount is:
Step a: bearing features point temperature and thermal deformation are extracted；
Step b: amendment lubricant viscosity and thermal induction pretightning force；
Step c: amendment rolling member heat amount.
Further, the specific method for correcting the variation of ambient temperature amount is:
Using temperature sensor measurement variation of ambient temperature, and measurement result is set to described configured with oscillating heat pipe
In high speed electric principal shaft system model.
Further, the thermal contact resistance of the bearing inner race and axle journal is corrected method particularly includes:
Step a: the radial heat distortion of axle journal and bearing inner race is extracted；
Step b: the variation of magnitude of interference between bearing inner race and axle journal is calculated；
Step c: the dynamic Contact thermal resistance during solution high-speed main spindle thermal balance between bearing inner race and axle journal.
Further, the specific method of the thermal contact resistance of the amendment bearing outer ring and bearing block is:
Step a: the mean temperature of bearing outer ring and bearing block is extracted；
Step b: the thermal contact resistance for extracting bearing outer ring and bearing block described in modified result is utilized.
Further, the convection transfer rate between the spindle unit and fluid is corrected method particularly includes:
Step a: characteristic point temperature and air themperature are extracted；
Step b: the convection transfer rate between characteristic point temperature and air themperature amendment spindle unit and fluid is utilized.
The beneficial effects of the present invention are:
The present invention provides configuration oscillating heat pipe electric chief axis system, advantage is to be provided with oscillating heat pipe in electro spindle,
With good heat exchange property, while present invention provides electric chief axis system thermal-structure coupled characteristics modeling method, with having
It limits first method and analyzes high speed electric principal shaft system thermal-structure coupled characteristic, advantage is to simulate the work shape of electric chief axis system
State guarantees axis system thermal-structure coupled limited features meta-model by way of amendment heat source load and thermal boundary condition
Modeling accuracy reduces the error of thermal-structure coupled specificity analysis, so that Finite element analysis results are closer to actual value.
Other advantages, target and feature of the invention will be illustrated in the following description to a certain extent, and
And to a certain extent, based on will be apparent to those skilled in the art to investigating hereafter, Huo Zheke
To be instructed from the practice of the present invention.Target and other advantages of the invention can be wanted by following specification and right
Book is sought to be achieved and obtained.
Detailed description of the invention
To make the objectives, technical solutions, and advantages of the present invention clearer, below in conjunction with attached drawing to the present invention make into
The detailed description of one step, in which:
Attached drawing 1 is high-speed electric main shaft structural schematic diagram；
Attached drawing 2 is the method for the present invention flow chart.
Specific embodiment
Hereinafter reference will be made to the drawings, and a preferred embodiment of the present invention will be described in detail.It should be appreciated that preferred embodiment
Only for illustrating the present invention, rather than limiting the scope of protection of the present invention.
The present invention provides configuration oscillating heat pipe electric chief axis systems, as shown in Figure 1, including main shaft housing 1, encoder 2, electricity
Machine stator 3, rotor 4 further include main shaft 5, are arranged inside main shaft housing 1, fore bearing 6 and rear bearing 7, realize main shaft 5
With the fixation of main shaft housing 1, main shaft 5 is connect with rotor 4, to realize the rotation of main shaft 5, the setting of 3 outer surface of motor stator
Cooling jacket 8 is arranged inside main shaft 5, oscillating heat pipe 9 is arranged between cooling jacket 8 and main shaft housing 1, with main shaft housing 1 one
The cooling device 10 of connection is held,
Cooling device 10 includes closure and passes through throttle valve 101, compressor 102, air pump 103 and chamber that pipeline 107 connects
Body 104, the pipeline 107 between air pump 103 and cavity 104 are set in cooling bath 105,
Oscillating heat pipe 9 protrudes into inside cavity 104 relative to 1 extension end of main shaft housing, and cooling gas is arranged inside cavity 104
106, for making oscillating heat pipe realize cold and hot exchange, the working medium inside oscillating heat pipe 9 is back and forth flowed.Compressor 102,
Air pump 103 realizes circulation of the cooling gas 106 inside cooling device 10, while throttle valve 101 adjusts closure aperture, can be with
The flowing velocity of cooling gas 106 is adjusted, and then changes the coefficient of heat transfer of oscillating heat pipe 9
As shown in Fig. 2, this method establishes operating condition ginseng the invention proposes a kind of modeling method of thermal-structure coupled characteristic
The heat source load model and thermal boundary condition of several and assembly parameter driving.Heat source load and thermal boundary condition are applied to numerical control machine
Bed heat-fluid-wall interaction specificity analysis model, is divided into multiple sub-steps for axis system thermal balance process, utilizes each sub-step point
It analyses obtained temperature field and numerically-controlled machine tool heat source load and thermal boundary condition is corrected in thermal deformation in real time.By revised heat source load
It is applied again to numerical control machine heat-fluid-wall interaction specificity analysis model with thermal boundary condition, Gu until numerical control machine heat-stream-coupling
Close the convergence of specificity analysis model.It is specific as follows:
Step 1: establishing the high speed electric principal shaft system model for being configured with oscillating heat pipe；
Step 2: applying heat source load in a model and thermal boundary condition, heat source load include thermal contact resistance, scrolling function
Component heat amount and variation of ambient temperature amount；
Thermal boundary condition includes that the convection current between the coefficient of heat transfer, thermal contact resistance and spindle unit and the fluid of oscillating heat pipe is changed
Hot coefficient, thermal contact resistance include the thermal contact resistance between bearing outer ring and bearing block thermal contact resistance and bearing inner race and axle journal.
Step 3: obtaining characteristic point temperature value；
Step 4: determine whether to meet the condition of convergence, the condition of convergence is shown in formula 1:
Ti-Ti-10.05~0.15 DEG C of formula 1 of <
Ti: the temperature of last moment characteristic point；
Ti-1: the temperature of this moment characteristic point.
Step 5: being computed, the temperature of characteristic point is not inconsistent box-like 1, is judged to not restraining, then carries out step 6；
Step 6: amendment heat source load and thermal boundary condition,
Amendment heat source load needs are modified S1 Rolling Components heat amount and S2 variation of ambient temperature amount, roll
Dynamic functional component heat amount is the function of lubricant viscosity, meanwhile, shadow of the Rolling Components heat amount by thermal induction pretightning force
It rings.
Step S11: extracting bearing features point temperature T and thermal deformation, thermal deformation include inner ring axial direction thermal walking δiThe outer ring and
Axial thermal walking δo；
Step S12: amendment lubricant viscosity v and thermal induction pretightning force Fa；
Lubricant kinematic viscosity v is the function of temperature, as shown in Equation 2:
V=32 × e-0.0242×(T-40)Formula 2
Thermal induction pretightning force FaWith inner ring axial direction thermal walking δiWith outer ring axial direction thermal walking δ0It is related, pass through FInite Element, meter
Initial heat source and shafting temperature field and thermal deformation under thermal boundary condition are calculated, the axial deflection of fore bearing Internal and external cycle is extracted, it can
To see that Internal and external cycle expands from inside to outside, bearing inner race deflection is big, and the difference of Internal and external cycle thermal walking is Δ δa, calculation method
It is as shown in Equation 3:
Δδa=δo-δiFormula 3
According to Bearing configuration and opening direction, whether analysis thermal walking is consistent to the direction of initial axial displacement, thus
Bearing axial displacement δ to after generation thermal deformationa:
δa=δpreload±ΔδaFormula 4
δpreload: the corresponding axial displacement/mm of initial pretightening force.
By the relational expression of axial displacement and contact angle, it is iterated with Newton-Raphson method and solves practical distortion
Bearing contact angle α afterwards:
Bring the actual contact angle α into following formula, the practical pretightning force F after acquiring thermal deformationa:
WhereinK is the axial displacement constant depending on total curvature B, can be checked in by chart.
Step S13: amendment rolling member heat amount.Bearing, that is, rolling member heat amount is as shown in Equation 7:
M=φishφrsMrr+Msl+Mseal+MdragFormula 7
In formula: Q --- bearing heating amount/W；M --- total frictional force square/Nmm；Mrr--- moment of rolling friction/N
mm；Msl--- sliding friction torque/Nmm；Mseal--- sealing element moment of friction/Nmm；Mdrag--- towing loss, whirlpool
Stream and the caused moment of friction/Nmm that splashes；φish--- incision fever reduces coefficient；φrs--- oil-poor backfill reduces system
Number.
Wherein MsealIt is the function of lubricant kinematic viscosity, MrrAnd MslIt is the function of pretightning force.
Moment of rolling friction MrrIt is as shown in Equation 8:
Mrr=Grr(νn)0.6Formula 8
In formula: Grr: rolling friction variable, it is related with bearing type, average diameter, load, it is shown in Table 1；N: revolving speed/r
min-1；ν: kinematic viscosity (viscosity that grease lubrication takes base oil)/mm of lubricant2·s-1。
Sliding friction torque is calculated according to formula 9:
Msl=GslμslFormula 9
In formula: Gsl: sliding friction variable, it is related with bearing type, average diameter, load, it is shown in Table 2；μsl: sliding friction
Coefficient, when lubricating condition is good, mineral oil lubrication takes 0.05, and synthesis oil lubrication takes 0.04.
The rolling of table 1, sliding friction variable
F in tablea, Fr: axially and radially load/N of bearing.
The above parameter is suitable for steel ball bearing, and Ceramic Balls elasticity modulus is high, small with steel raceway contact face, thus rolls and slide
Dynamic friction is smaller.Meanwhile ceramic density is small, rotation centrifugal force is small, so it is small to rub in high speed.When calculating ceramic ball bearing,
R3And S30.41 is taken, the formula for calculating moment of friction further according to steel ball bearing calculates.
Bearing with contact seal part can be calculated by the moment of friction that sealing element and lasso contact generate according to formula 10:
Mseal=KS1dS β+KS2Formula 10
In formula: KS1: constant related with bearing type is shown in Table 2；KS2: constant related with bearing seal type is shown in Table
2；dS: diameter/mm of bearing shoulder is shown in Table 2；β: index related with bearing and sealing ring type is shown in Table 2.
2 sealing element moment of friction calculating parameter of table
Note: d1For bearing inner race outer diameter；For there was only the bearing of side sealing ring, moment of friction 0.5Mseal。
The bearing of bath lubrication must be taken into consideration by lubricating oil towing, vortex and moment of friction caused by splashing；Rouge is moistened
Sliding and oil-air lubrication, it is believed that towing loss is 0.It can when calculating its towing moment of friction for the bearing of fog lubrication
The calculation method of oil-bath lubrication, as shown in Equation 11:
Mdrag=VMKballdm 5n2Formula 11
In formula: VM: towing loss variable, it is related with oil level H and bearing average diameter, it pulls and damages referring to SKF bearing handbook
Lose variable curve；Kball: ball bearing constant, calculation formula are as follows:
In formula: irw: bearing ball columns；KZ: constant related with bearing type takes 4.4 for single-row angular contact ball bearing；
D: bearing outside diameter/mm；D: bearing bore diameter/mm.
Only have minimal amount of lubricant to form oil film in bearing, partially the lubricating oil close to the contact site side Ru You is extruded
It is formed and is flow backwards, in the inside of refluence because shear action generates heat, lubricating oil viscosity reduces at any time, and then oil film thickness and rolling rub
It wipes and reduces.It introduces incision fever and reduces coefficient to express this reduction trend:
In oil-air lubrication, fog lubrication and grease lubrication, excessive lubricant, while axis can be squeezed out when roller presses through raceway
Holding high rotational speed or the excessively high situation of lubricant viscosity can prevent lubricant from roller and raceway contact position is replenished in time,
Reduce so as to cause oil film thickness and rolling friction, here it is " movement is oil-poor " phenomenon, oil-poor backfill reduces coefficient and presses following public affairs
Formula calculates:
In formula: Krs: oil-poor backfill constant, oil-air lubrication and grease lubrication take 6 × 10-8, fog lubrication takes 4 × 10-8。
During axis system thermal balance, environment temperature is in variation.
The specific method of S2 amendment environment temperature variation is: using temperature sensor measurement variation of ambient temperature, and will
Measurement result is set in the high speed electric principal shaft system model configured with oscillating heat pipe.
Amendment thermal boundary condition need between N1 thermal contact resistance, N2 spindle unit and fluid convection transfer rate and
Be modified, wherein thermal contact resistance include N11 bearing outer ring and bearing block thermal contact resistance and N12 bearing inner race and axle journal it
Between thermal contact resistance.
The amendment of N11 bearing outer ring and bearing block thermal contact resistance, specifically includes:
Step N111: the mean temperature T of bearing outer ring and bearing block is proposedring and Thousing；
Step N112: amendment bearing outer ring and bearing block thermal contact resistance, thermal contact resistance R are as shown in Equation 15:
Wherein, δringIndicate the thickness of bearing outer ring；λairAnd λringRespectively indicate the thermal conductivity of air and bearing outer ring material
Rate；δgapIt indicates the gap between bearing outer ring and bearing block, is expressed as formula 16:
δgap=δgap0-(Tring-Thousing)·α·rhousingFormula 16
δ in formulagap0Indicate primary clearance, α indicates thermal stretching rate；rhousingIndicate bearing block radius.
The amendment of thermal contact resistance between N12 bearing inner race and axle journal.Thermal contact resistance between bearing inner race and axle journal is
The function of magnitude of interference.Magnitude of interference generates variation with the thermal deformation of axle journal and bearing inner race,
Therefore, step N121 needs to obtain axle journal radial deformation δsWith bearing inner race radial deformation δd, substitute into formula 17, ask
Value of interference fit changing value Δ out, which, which is positive, indicates that magnitude of interference increases, and being negative indicates that magnitude of interference reduces.
Δ=δs-δdFormula 17
δs: the axle journal radial heat distortion with inner ring cooperation, μm；
δd: bearing inner race radial heat distortion, μm；
Δ: value of interference fit changing value, μm.
Step N122: according to magnitude of interference changing value Δ, finding out magnitude of interference, as shown in Equation 18,
E1: bearing inner race elasticity modulus of materials；
E2: axle journal elasticity modulus of materials；
D1: bearing inner race diameter；
D2: journal diameter；
D3: spindle shaft in-core diameter；
v1: bearing inner race material Poisson's ratio；
v1: axle journal material Poisson's ratio.
Step N123: the dynamic Contact thermal resistance during solution thermal balance between bearing inner race and axle journal.
Bearing inner race and journal contact thermal resistance indicate are as follows:
Wherein, k1And k2Indicate the thermal conductivity of bearing inner race and axle journal；AaIndicate nominal contact area；kfIt indicates in gap
Medium heat conductance；δvIndicate gap thickness；AcIndicate real contact area；AvIndicate interval area.
Real contact area AcIt indicates are as follows:
Gap thickness δvIt indicates are as follows:
δv=2 (z-GD-1aL (2-D2)) formula 21
Contact load on contact interface indicates are as follows:
Contact load and external load balance, it may be assumed that
F=Fex=pAaFormula 23
Thermal contact resistance RcWith real contact area AcIt is Maximum Contact area aLFunction.It can recognize to obtain by formula 22 and 23
Maximum Contact area aL.Due to rotary shaft and bearing temperature difference, linear expansion coefficient is also different, can make rotary shaft outside cylinder
Face and bearing inner race radial heat distortion are of different sizes, change so as to cause matching allowance.Shafting thermal deformation analysis can be with
Predict the variation of bearing and axis the initial engagement use level after temperature raising in actual rotation.With caused by temperature change
Variable quantity provides corresponding fit dimension offset when starting design, to guarantee still to have after actual work temperature changes
Excellent cooperation.
Convection transfer rate between N2 spindle unit and fluid is the function of spindle unit temperature.It is flat in high-speed main spindle heat
Spindle unit temperature gradually rises during weighing apparatus, finally tends towards stability.So the heat convection system between spindle unit and fluid
Number is among dynamic change.Therefore, the convection transfer rate between spindle unit and fluid is corrected specifically:
Step a: axis system thermal-structure coupled specificity analysis result is extracted；
Obtaining widget temperature T and air themperature TaBetween difference, be denoted as Δ t, it may be assumed that
Δ t=T-TaFormula 24
Δ t: the difference between part temperatures and air themperature, DEG C；
T: part temperatures, DEG C；
Ta: air themperature, DEG C.
Step b: the convection transfer rate extracted between modified result spindle unit and fluid is utilized.
Convection coefficient can be indicated with formula 25:
λ is fluid thermal conductivity；
L indicates hydraulic radius；
Nu indicates nusselt number.
Wherein, the representation method of Nu is as shown in Equation 26:
Wherein, m and n indicates the constant by determining towards heat-transfer surface；Gr and Pr respectively indicate grashof number and Prandtl
Number；C indicates constant.
The representation method of Gr is as shown in Equation 27:
G indicates acceleration of gravity；β2Indicate the thermal stretching coefficient of fluid；V indicates kinematic viscosity.
By formula 25~27, the amendment of the convection transfer rate between spindle unit and fluid can be completed.
It is completed through the above way to thermal contact resistance, convection transfer rate, Rolling Components heat amount and environment temperature
Variation amendment, correction result is inputted in corresponding thermal boundary condition and heat source load, continues to verify whether to meet the condition of convergence,
If not restraining, continue to correct thermal boundary condition and heat source load, until convergence, after determining convergence, carries out step 5.
Step 5: drawing out the temperature curve of characteristic point.
Finally, it is stated that the above examples are only used to illustrate the technical scheme of the present invention and are not limiting, although referring to compared with
Good embodiment describes the invention in detail, those skilled in the art should understand that, it can be to skill of the invention
Art scheme is modified or replaced equivalently, and without departing from the objective and range of the technical program, should all be covered in the present invention
Scope of the claims in.
Claims (10)
1. configuring oscillating heat pipe electric chief axis system, including main shaft housing, encoder, motor stator, rotor, feature exist
In: further include,
Main shaft is arranged inside the main shaft housing,
Fore bearing and rear bearing realize the fixation of main shaft and main shaft housing,
The main shaft is connect with rotor, to realize the rotation of the main shaft,
Cooling jacket is arranged in the motor stator outer surface；
Oscillating heat pipe is arranged inside the main shaft, between the cooling jacket and the main shaft housing in setting,
The cooling device being connect with one end of the main shaft housing,
The cooling device includes throttle valve, compressor, air pump and the cavity for being closed and being connected by pipeline, the air pump and chamber
Pipeline between body is set in cooling bath,
The oscillating heat pipe protrudes into the inside cavity relative to the main shaft housing extension end,
Cooling gas is arranged in the inside cavity.
2. a kind of thermal-structure coupled characteristics modeling method of electric chief axis system as described in claim 1, it is characterised in that: institute
State modeling method specifically:
Step 1: establishing the high speed electric principal shaft system model for being configured with oscillating heat pipe；
Step 2: calculating and apply heat source load and thermal boundary condition in a model；
Step 3: obtaining characteristic point temperature value；
Step 4: determine whether to meet the condition of convergence,
Step 5: if convergence, draws temperature variation curve, terminating；If not restraining, step 6 is carried out；
Step 6: amendment heat source load and thermal boundary condition, return step 3.
3. a kind of thermal-structure coupled characteristics modeling method according to claim 2, it is characterised in that: the heat source load
Including motor heat amount, Rolling Components heat amount and variation of ambient temperature amount.
4. a kind of thermal-structure coupled characteristics modeling method according to claim 2, it is characterised in that: the thermal boundary item
Part includes the convection transfer rate between the oscillating heat pipe coefficient of heat transfer, thermal contact resistance and spindle unit and fluid, the contact heat
Resistance includes the thermal contact resistance and bearing inner race of bearing outer ring and bearing block and the thermal contact resistance of axle journal.
5. a kind of thermal-structure coupled characteristics modeling method according to claim 2, it is characterised in that: the decision condition
Are as follows:
Ti-Ti-10.05~0.15 DEG C of <
Ti: the temperature of characteristic point described in last moment；
Ti-1: the temperature of characteristic point described in this moment.
6. a kind of thermal-structure coupled characteristics modeling method according to claim 3, it is characterised in that: correct the rolling
The specific method of functional component heat amount is:
Step a: bearing features point temperature and thermal deformation are extracted；
Step b: amendment lubricant viscosity and thermal induction pretightning force；
Step c: amendment rolling member heat amount.
7. a kind of thermal-structure coupled characteristics modeling method according to claim 3, it is characterised in that: correct the environment
The specific method of temperature variation is:
The high speed for being configured with oscillating heat pipe is set to using temperature sensor measurement variation of ambient temperature, and by measurement result
In electric chief axis system model.
8. a kind of thermal-structure coupled characteristics modeling method according to claim 4, it is characterised in that: correct the bearing
The thermal contact resistance of inner ring and axle journal method particularly includes:
Step a: the radial heat distortion of axle journal and bearing inner race is extracted；
Step b: the variation of magnitude of interference between bearing inner race and axle journal is calculated；
Step c: the dynamic Contact thermal resistance during solution high-speed main spindle thermal balance between bearing inner race and axle journal.
9. a kind of thermal-structure coupled characteristics modeling method according to claim 4, it is characterised in that: the amendment bearing
The specific method of the thermal contact resistance of outer ring and bearing block is:
Step a: the mean temperature of bearing outer ring and bearing block is extracted；
Step b: the thermal contact resistance for extracting bearing outer ring and bearing block described in modified result is utilized.
10. a kind of thermal-structure coupled characteristics modeling method according to claim 4, it is characterised in that: correct the main shaft
Convection transfer rate between component and fluid method particularly includes:
Step a: characteristic point temperature and air themperature are extracted；
Step b: the convection transfer rate between characteristic point temperature and air themperature amendment spindle unit and fluid is utilized.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111273605A (en) * | 2020-03-04 | 2020-06-12 | 上海交通大学 | Intelligent electric spindle system of numerical control machine tool |
| CN113051686A (en) * | 2021-04-01 | 2021-06-29 | 重庆大学 | Spindle system thermal-structure coupling characteristic model creation method and thermal error model modeling method under inclined working condition |
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| CN111273605A (en) * | 2020-03-04 | 2020-06-12 | 上海交通大学 | Intelligent electric spindle system of numerical control machine tool |
| CN111273605B (en) * | 2020-03-04 | 2022-01-04 | 上海交通大学 | Intelligent electric spindle system of numerical control machine tool |
| CN113051686A (en) * | 2021-04-01 | 2021-06-29 | 重庆大学 | Spindle system thermal-structure coupling characteristic model creation method and thermal error model modeling method under inclined working condition |
| CN113051686B (en) * | 2021-04-01 | 2023-03-10 | 重庆大学 | Spindle system thermal-structure coupling characteristic model creation method and thermal error model modeling method under inclined working condition |
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