CN106289773A - A kind of determination method of machine tool mainshaft bearing radially non-linear rigidity - Google Patents

A kind of determination method of machine tool mainshaft bearing radially non-linear rigidity Download PDF

Info

Publication number
CN106289773A
CN106289773A CN201610560541.9A CN201610560541A CN106289773A CN 106289773 A CN106289773 A CN 106289773A CN 201610560541 A CN201610560541 A CN 201610560541A CN 106289773 A CN106289773 A CN 106289773A
Authority
CN
China
Prior art keywords
bearing
main shaft
radial
rigidity
spindle
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.)
Granted
Application number
CN201610560541.9A
Other languages
Chinese (zh)
Other versions
CN106289773B (en
Inventor
李小虎
朱雷
张燕飞
吕义发
李森
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Xian Jiaotong University
Original Assignee
Xian Jiaotong University
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Xian Jiaotong University filed Critical Xian Jiaotong University
Priority to CN201610560541.9A priority Critical patent/CN106289773B/en
Publication of CN106289773A publication Critical patent/CN106289773A/en
Application granted granted Critical
Publication of CN106289773B publication Critical patent/CN106289773B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings

Abstract

The determination method of a kind of machine tool mainshaft bearing of the present invention radially non-linear rigidity, it is considered to the actual stand under load impact on bearing rigidity, determines the main shaft bearing radial rigidity of actual stand under load by round-about way.Comprising the steps, step 1 sets up main shaft stress model；It is calculated main shaft support reaction suffered by each bearing under difference radially power effect；Step 2 sets up bearing five degree of freedom mechanical model；Obtain each bearing radial rigidity under current radial force effect；Step 3 sets up main shaft power FEM (finite element) model, obtains current radial force effect lower main axis front end dynamic stiffness and the corresponding relation of all bearing radial rigidities；Step 4 sets up front-end of spindle dynamic stiffness and the corresponding relation data base of all bearing radial rigidities；Step 5 is tested by main shaft dynamic stiffness, applies test radial load at front-end of spindle, obtains the dynamic stiffness of setting speed lower main axis front end, inquire about in corresponding relation data base, obtain the radial rigidity of all bearings under main shaft practical situation.

Description

A kind of determination method of machine tool mainshaft bearing radially non-linear rigidity
Technical field
The present invention relates to the performance test application of machine tool mainshaft bearing, be specially a kind of machine tool mainshaft bearing the most non- The determination method of linear rigidity
Background technology
Bearing rigidity is one of most important parameter of main shaft bearing, generally provides only in the catalogue of bearing mnanufacture manufacturer Its static axial stiffness under underloading, middle load and fully loaded transportation condition.The radial rigidity of bearing for crudy guarantee the most very Important, and bearing radial rigidity is nonlinear, changes along with the change of the factor such as the speed of mainshaft, suffered outer load.
Machine tool chief axis is during actual cut, and main shaft would generally driven power and cutting force.In many instances, pass Power and cutting force are all to act on main shaft as radial force, as shown in Figure 2.Main shaft is when bearing radial load, and bearing is also Can be by corresponding radially support reaction, bearing radial rigidity has non-linear, and radial rigidity is very big on crudy impact, Such as during bore hole, main shaft radial rigidity directly affects physical dimension and the surface quality of bore hole.It is thus determined that bearing exists Radial rigidity under loading conditions has great importance for instructing processing.
At present, determine that the method for bearing radial rigidity is usually according to the pretightning force under original state, seldom consider bearing The impact on bearing radial rigidity of the actual stand under load.
Summary of the invention
For problems of the prior art, the present invention provides a kind of machine tool mainshaft bearing radially non-linear rigidity really Determine method, it is considered to the impact on bearing rigidity of the actual stand under load, determined the main shaft bearing footpath of actual stand under load by round-about way To rigidity.
The present invention is to be achieved through the following technical solutions:
The determination method of a kind of machine tool mainshaft bearing radially non-linear rigidity, comprises the steps,
Step 1, sets up main shaft stress model；By applying radial load at front-end of spindle, axis system is carried out load Analyze, be calculated main shaft support reaction suffered by each bearing under difference radially power effect；
Step 2, sets up bearing five degree of freedom mechanical model；Calculate the corresponding support reaction effect in step 1 of each bearing Under radial rigidity, thus obtain each bearing radial rigidity under current radial force effect；
Step 3, sets up main shaft power FEM (finite element) model, the radial rigidity of all bearings under current radial force effect is added It is added on the node that in main shaft power FEM (finite element) model, main shaft is corresponding；Under different rotating speeds, carry out analysis of Dynamic Stiffness, obtain Front-end of spindle dynamic stiffness, obtains the corresponding pass of current radial force effect lower main axis front end dynamic stiffness and all bearing radial rigidities System；
Step 4, sets up front-end of spindle dynamic stiffness and the corresponding relation data base of all bearing radial rigidities, by conversion footpath To load, step 1 being repeated several times and arrives step 3, analyze and obtain under different rotating speeds, under different radially power effects, front-end of spindle is dynamic firm Degree and the corresponding relation of all bearing radial rigidities, thus set up corresponding relation data base；
Step 5, is tested by main shaft dynamic stiffness, applies test radial load at front-end of spindle, and test obtains setting speed The dynamic stiffness of lower main axis front end, is input to the dynamic stiffness obtained in the corresponding relation data base obtained in step 4 inquire about, Obtain main shaft in the actual course of processing, consider the radial rigidity of all bearings under each bearing loading conditions.
Preferably, in step 1, when axis system is carried out loading analysis, comprise the following steps that,
First, axis system is carried out dividing elements, with at front-end of spindle stress, at diameter of axle change and all bearings prop up Being node at support point, the part between adjacent node is a unit；
Then, the stiffness matrix of each unit it is calculated；The stiffness matrix superposition of all unit is obtained main shaft system The global stiffness matrix of system；
Finally, the stress balance equation of axis system the support reaction of each bearing corresponding node is obtained.
Preferably, comprising the following steps that of step 2,
First, bearing five is acted on freely by the rotating speed preset and step 1 solve each bearing support reaction obtained In degree mechanical model, according to Harris bearing five degree of freedom bearing theory, set up bearing five degree of freedom quasi-static testing rigidity model；
Then, according to five degree of freedom quasi-static testing rigidity model, solve the five degree of freedom stiffness matrix obtaining each bearing, Thus obtain bearing radial rigidity under corresponding support reaction and under preset rotation speed.
Preferably, the concrete step by main shaft power FEM (finite element) model, the dynamic stiffness of main shaft being analyzed in step 3 It is rapid as follows,
Step 3.1, main shaft pretreatment, by hole, groove and screw thread by entity handles, chamfering will be simplified to right angle everywhere, ignore Escape；
Step 3.2, bearing equivalent process, each bearing is equivalent to four radially-arranged spring units；Wherein, spring The difference of the Internal and external cycle radius of a length of bearing, spring position is on the intersection point of main-shaft axis and bearing normal；Spring unit firm Degree is calculated Rigidity Matrix of Bearings in step 2；
Step 3.3, main shaft load applies, and applies radial load at front-end of spindle and arranges the speed of mainshaft and second step In preset rotation speed；Add eccentric mass at front-end of spindle, main shaft is carried out analysis of Dynamic Stiffness, obtains front-end of spindle dynamic stiffness meter Calculation model is as follows,
K d ( ω ) = meω 2 δ ;
Wherein, m is eccentric mass, and e is the center of gravity eccentric throw relative to main shaft rotation center of eccentric mass, and ω is main shaft Rotating speed, δ is the radial displacement of front-end of spindle.
Further, comprising the following steps that of step 4,
According to the front-end of spindle dynamic stiffness computation model obtained in step 1 to step 3, by arranging the different speed of mainshaft With the dynamic stiffness that the rigidity of spring unit calculates front-end of spindle, thus set up front-end of spindle dynamic stiffness and bearing radial rigidity Corresponding relation data base.
Further, comprising the following steps that of step 5,
Use dynamic balance instrument that main shaft is carried out spot dynamic balance experiment with measuring, obtain the centroid offset of main shaft, use position Displacement sensor obtains the radial displacement of corresponding rotating speed lower main axis front end, before obtaining main shaft according to front-end of spindle dynamic stiffness computation model The dynamic stiffness of end, is input to the dynamic stiffness obtained in the corresponding relation data base that step 4 obtains inquire about, obtains main shaft and exist The actual course of processing considers the radial rigidity of all bearings under each bearing loading conditions.
Further, in step 5 during dynamic balancing measurement test, it is the counterweight screws of m at front-end of spindle installation quality, counterweight The center of gravity of screw and the eccentric throw of main shaft rotation center are e；At counterweight screws front plan for measuring plane, in measuring plane Along Y-direction cloth displacement sensor, displacement transducer vertical major axis is the most consistent with radial direction external applied load applying direction, to measure Main shaft radial displacement；Choose applying external load function point at front-end of spindle, a bearing, bearing inner race and master are installed at application point Axle is fixed, and outer ring contacts with hydraulic cylinder, and hydraulic cylinder applies radially external applied load, and force direction is Y-direction；Start main shaft and master is set Axle rotating speed is ω, after spindle operation is stable, reads displacement transducer registration, will letter by signal sampler and signal processing instrument Number it is input in computer, obtains front-end of spindle dynamic stiffness according to front-end of spindle dynamic stiffness computation model.
Compared with prior art, the present invention has a following useful technique effect:
First the present invention carries out loading analysis to main shaft, obtains main shaft anti-at suffered by Different Diameter outwards load effect lower bearing Power；Then set up bearing five degree of freedom mechanical model, obtain bearing radial rigidity under above-mentioned support reaction active force；By dynamic Mechanics finite element analysis, is obtained front-end of spindle dynamic stiffness and bearing radial rigidity corresponding relation data base, is surveyed by field experimentation Obtain and use state exist front-end of spindle dynamic stiffness in the case of footpath outwards carries, by the dynamic stiffness that obtains above-mentioned main shaft dynamic stiffness with The data base of bearing radial rigidity inquires about, finally tries to achieve corresponding bearing radial rigidity.The present invention measures bearing radial rigidity Method consider the impact on bearing rigidity of the machine tool chief axis actual stand under load, measurement result is accurate, and actual to machine tool chief axis adds Instrument has directive significance.
Accompanying drawing explanation
Fig. 1 is the determination method flow diagram of machine tool mainshaft bearing radial rigidity described in present example.
Fig. 2 is front-end of spindle described in present example by after radial load, axle system deformation schematic diagram.
Fig. 3 is four bearings-rotor-support-foundation system described in present example.
Fig. 4 is four bearings described in present example-rotor-support-foundation system dividing elements figure.
Fig. 5 is main shaft power FEM (finite element) model figure described in present example.
Fig. 6 is FEM (finite element) model middle (center) bearing described in present example-spring equivalent schematic.
Fig. 7 is that main shaft dynamic stiffness measurement described in present example tests schematic diagram.
In figure, main shaft 1, hydraulic cylinder 2, bearing 3, counterweight screws 4, displacement transducer 5.
Detailed description of the invention
Below in conjunction with specific embodiment, the present invention is described in further detail, described in be explanation of the invention and It not to limit.
The determination method of a kind of machine tool mainshaft bearing of the present invention radially non-linear rigidity, as it is shown in figure 1, it includes following step Rapid:
Set up main shaft stress model, by applying a radial load at front-end of spindle, axis system carried out loading analysis, Hold the support reaction of corresponding node based on Shaft system analysis Finite element arithmetic shaft, thus obtain main shaft in the outwards load effect of this footpath Under support reaction suffered by each bearing；
Set up bearing five degree of freedom mechanical model, calculate each bearing radial direction under the support reaction effect of above-mentioned correspondence firm Degree, thus obtain each bearing radial rigidity under this radial force effect；
Set up main shaft power FEM (finite element) model, add above-mentioned each bearing radial rigidity to main shaft power finite element mould In type in main shaft respective nodes, under different rotating speeds, carry out analysis of Dynamic Stiffness, obtain front-end of spindle dynamic stiffness, obtain this footpath To power effect lower main axis front end dynamic stiffness and the corresponding relation of each bearing radial rigidity；Set up front-end of spindle dynamic stiffness and bearing footpath To the fit correlation data base that rigidity is corresponding, transformation load repeat the above steps, repeatedly carry out above-mentioned analysis, obtain carrying in difference Lotus and different rotating speeds lower main axis front end dynamic stiffness and the corresponding relation of each bearing radial rigidity, thus set up corresponding relation data Storehouse；
Being tested by main shaft dynamic stiffness, apply certain load at front-end of spindle, test obtains corresponding rotating speed lower main axis front end Dynamic stiffness, so that it is determined that there is the dynamic stiffness of front-end of spindle in the case of footpath outwards carries, the dynamic stiffness obtained is input to above-mentioned Corresponding relation data base inquires about, obtains considering all bearings under each bearing loading conditions in the actual course of processing of main shaft Radial rigidity.
Comprise the following steps that described.
First, set up main shaft stress model, apply radial load at front-end of spindle, based on Shaft system analysis FInite Element, really The stiffness matrix of each node of dead axle system, solve front-end of spindle the support reaction on each bearing loaded.As it is shown on figure 3, this is System structure belongs to redundant structure, a lot of in the case of spindle rotor system broadly fall into this structure.First it is carried out unit Divide, be divided into 4 unit, 5 nodes, unit and node respectively with 1., 2., 3., 4. with 1,2,3,4,5 represent, 5 nodes It is respectively front end stress point and the strong point at four bearings is set.As shown in Figure 4, for any of which unit, correspondence Stiffness matrix is:
K i = EI i L i 12 L i 2 - 6 L i - 12 L i 2 - 6 L i - 6 L i 4 6 L i 2 - 12 L i 2 6 L i 12 L i 2 6 L i - 6 L i 2 6 L i 4 ;
In formula, E is the elastic modelling quantity of material, and I is the moment of inertia of beam section, for circular cross-section, as a diameter of D, has:
I = πD 4 64 ;
The global stiffness matrix of system is formed by stacking by the stiffness matrix of all unit.Thus list system stress balance side Journey:
KU=P；
In formula, U is motion vector, and P is load vectors, and K is the global stiffness matrix of spindle bearing system.By system stress Equilibrium equation obtains motion vector U, then utilizes following formula in the unit corresponding to bearing,
KbUb=Pb；
Try to achieve the support reaction of each bearing corresponding node.
In formula, KbFor the stiffness matrix of bearing place unit, UbFor the motion vector of bearing place unit, PbFor bearing institute Load vectors at unit；
Second, set up bearing five degree of freedom mechanical model, solve each bearing support reaction of obtaining by above-mentioned and preset Rotating speed acts in bearing five degree of freedom mechanical model, according to Harris bearing five degree of freedom bearing theory, sets up contact ball axle Hold five degree of freedom quasi-static testing rigidity model.In Five-degree-of-freedom spatial, available [Δ x, Δ y, Δ z, Δ θy,Δθz] represent The displacement of the axial x of bearing, radially y, radially z and around y-axis and the corner of z-axis.Corresponding with displacement, with [Fx,Fy,Fz,My, Mz] represent the stress of the axial x of bearing, radially y, radially z and around y-axis and the torque of z-axis.According to five degree of freedom quasi-static testing Rigidity Calculation model solves [Δ x, Δ y, Δ z, Δ θy,Δθz], all directions power is sought local derviation respectively, obtains bearing five freely Degree stiffness matrix Kz。
K z = ∂ F x / ∂ x ∂ F x / ∂ y ∂ F x / ∂ z ∂ F x / ∂ θ y ∂ F x / ∂ θ z ∂ F y / ∂ x ∂ F y / ∂ y ∂ F y / ∂ z ∂ F y / ∂ θ y ∂ F y / ∂ θ z ∂ F z / ∂ x ∂ F z / ∂ y ∂ F z / ∂ z ∂ F z / ∂ θ y ∂ F z / ∂ θ z ∂ M y / ∂ x ∂ M y / ∂ y ∂ M y / ∂ z ∂ M y / ∂ θ y ∂ M y / ∂ θ z ∂ M z / ∂ x ∂ M z / ∂ y ∂ M z / ∂ z ∂ M z / ∂ θ y ∂ M z / ∂ θ z ;
Thus obtain bearing radial rigidity under corresponding support reaction and under preset rotation speed.
3rd, set up main shaft power FEM (finite element) model, add eccentric mass in main shaft model front end.Second step is calculated The bearing radial rigidity obtained is added in main shaft power FEM (finite element) model, carries out analysis of Dynamic Stiffness, really under different rotating speeds Determine under different rotating speeds, front-end of spindle dynamic stiffness and the corresponding relation of bearing radial rigidity；
Calculate in main shaft power FEM (finite element) model specifically comprises the following steps that
Step 3.1, main shaft pretreatment, shown in Fig. 5, by hole, groove, screw thread etc. by entity handles, will chamfering be simplified to everywhere Right angle, ignores escape.So can improve solving speed on the premise of not affecting result of calculation.
Step 3.2, bearing equivalent process, bearing is equivalent to 4 radially-arranged spring units, as shown in Figure 6.Spring The difference of the Internal and external cycle radius of a length of bearing, spring position is on the intersection point of main-shaft axis and bearing normal.Spring unit firm Degree is calculated bearing radial rigidity in second step,
K r = ∂ F y ∂ y
Step 3.3, main shaft load applies, and applies radial load F at front-end of spindlesAnd the speed of mainshaft and second step are set In rotating speed corresponding.Add eccentric mass m at axle head, main shaft is carried out analysis of Dynamic Stiffness, obtains front-end of spindle dynamic stiffness such as Under,
K d ( ω ) = meω 2 δ ;
Wherein e is the center of gravity eccentric throw relative to main shaft rotation center of eccentric mass, and ω is the speed of mainshaft, and δ is main shaft The radial displacement of front end.
4th, in dynamic stiffness computation model, calculate front-end of spindle by arranging different rotating speeds and spring stiffness values Dynamic stiffness value；Under many group main shaft radial loads, determine corresponding each bearing rigidity, each bearing rigidity organized is added respectively It is added in main shaft power FEM (finite element) model, is calculated the front-end of spindle dynamic stiffness of correspondence, thus sets up front-end of spindle and move The corresponding relation data base of rigidity and bearing radial rigidity.
5th, carry out main shaft dynamic stiffness experiment, use dynamic balance instrument that main shaft is carried out spot dynamic balance experiment with measuring, obtain The centroid offset of main shaft, arranges the speed of mainshaft, uses displacement transducer to obtain the radial displacement of corresponding rotating speed lower main axis front end, Calculate the dynamic stiffness of front-end of spindle according to dynamic stiffness definitional relation in step 3.3, the dynamic stiffness obtained is input to the 4th step In front-end of spindle dynamic stiffness and bearing radial rigidity corresponding relation data base in, obtain bearing under bearing loading condition Radial rigidity.
During concrete operations, as it is shown in fig. 7, at the counterweight screws 4 that front-end of spindle appropriate location installation quality is m, counterweight spiral shell The center of gravity of nail 4 is e with the eccentric throw of main shaft 1 centre of gyration.Choosing measurement plane in the anterior appropriate location of counterweight screws 4, this is excellent Select in example with counterweight screws front plan for measuring plane.Along Y-direction cloth displacement sensor 5, displacement in measuring plane Sensor 5 vertical major 1 axis is also fixed on support to measure main shaft 1 radial displacement, chooses in appropriate location, main shaft 1 front end Apply external load function point；Effect is pointed out and is provided with a bearing 3, and bearing 3 inner ring is fixed with main shaft 1, and outer ring connects with hydraulic cylinder 2 Touch, to ensure that, when main axis, radial force loading force is reliable and stable.Hydraulic cylinder 2 applies external applied load as charger, makees Power thrusts is Y-direction；Loading position is positioned at immediately below front-end of spindle, and loading procedure should be slow, cylinder device to be loaded Measure again after Wen Ding.Start main shaft 1 arranging the speed of mainshaft is ω, after main shaft 1 operating is stable, reads displacement transducer 5 Registration, is input a signal in computer 8 by signal sampler 6 and signal processing instrument 7, obtains front-end of spindle dynamic stiffness.? Front-end of spindle dynamic stiffness is input in main shaft dynamic stiffness and bearing radial rigidity corresponding relation data base inquiry, obtains bearing radially Rigidity.Wherein, outwards carry direction with footpath identical and be perpendicular to main-shaft axis for displacement transducer 5.
This preferred embodiment uses following critical piece: displacement transducer: MTI company of the AS-500 U.S.；Dynamic balance instrument: KMPDM company of the KMbalancer U.S.；Hydraulic cylinder: RD-41 hydraulic cylinder.
The foregoing is only one embodiment of the present invention, be not all of or unique embodiment, this area is common The conversion of any equivalence that technical solution of the present invention is taked by technical staff by reading description of the invention, is the present invention Claim contained.

Claims (7)

1. the determination method of a machine tool mainshaft bearing radially non-linear rigidity, it is characterised in that comprise the steps,
Step 1, sets up main shaft stress model；By applying radial load at front-end of spindle, axis system is carried out loading analysis, It is calculated main shaft support reaction suffered by each bearing under difference radially power effect；
Step 2, sets up bearing five degree of freedom mechanical model；Calculate under the corresponding support reaction effect in step 1 of each bearing Radial rigidity, thus obtain each bearing radial rigidity under current radial force effect；
Step 3, sets up main shaft power FEM (finite element) model, the radial rigidity of all bearings under current radial force effect is added to On the node that in main shaft power FEM (finite element) model, main shaft is corresponding；Under different rotating speeds, carry out analysis of Dynamic Stiffness, obtain main shaft Front end dynamic stiffness, obtains current radial force effect lower main axis front end dynamic stiffness and the corresponding relation of all bearing radial rigidities；
Step 4, sets up front-end of spindle dynamic stiffness and the corresponding relation data base of all bearing radial rigidities, is radially carried by conversion Lotus, is repeated several times step 1 to step 3, analyzes and obtain under different rotating speeds, under different radially power effects, front-end of spindle dynamic stiffness and The corresponding relation of all bearing radial rigidities, thus set up corresponding relation data base；
Step 5, is tested by main shaft dynamic stiffness, applies test radial load at front-end of spindle, and test obtains under setting speed main The dynamic stiffness of axle front end, is input to the dynamic stiffness obtained in the corresponding relation data base obtained in step 4 inquire about, obtains Main shaft considers the radial rigidity of all bearings under each bearing loading conditions in the actual course of processing.
The determination method of a kind of machine tool mainshaft bearing the most according to claim 1 radially non-linear rigidity, it is characterised in that In step 1, when axis system is carried out loading analysis, comprise the following steps that,
First, axis system is carried out dividing elements, with at front-end of spindle stress, at diameter of axle change and all bearings point Place is node, and the part between adjacent node is a unit；
Then, the stiffness matrix of each unit it is calculated；The stiffness matrix superposition of all unit is obtained axis system Global stiffness matrix；
Finally, the stress balance equation of axis system the support reaction of each bearing corresponding node is obtained.
The determination method of a kind of machine tool mainshaft bearing the most according to claim 1 radially non-linear rigidity, it is characterised in that Comprising the following steps that of step 2,
First, bearing five degree of freedom power is acted on by the rotating speed preset and step 1 solve each bearing support reaction obtained Learn in model, according to Harris bearing five degree of freedom bearing theory, set up bearing five degree of freedom quasi-static testing rigidity model；
Then, according to five degree of freedom quasi-static testing rigidity model, solve the five degree of freedom stiffness matrix obtaining each bearing, thus Obtain bearing radial rigidity under corresponding support reaction and under preset rotation speed.
The determination method of a kind of machine tool mainshaft bearing the most according to claim 1 radially non-linear rigidity, it is characterised in that By main shaft power FEM (finite element) model to comprising the following steps that the dynamic stiffness of main shaft is analyzed in step 3,
Step 3.1, main shaft pretreatment, by hole, groove and screw thread by entity handles, chamfering will be simplified to right angle everywhere, ignore withdrawing Groove；
Step 3.2, bearing equivalent process, each bearing is equivalent to four radially-arranged spring units；Wherein, its length For the difference of the Internal and external cycle radius of bearing, spring position is on the intersection point of main-shaft axis and bearing normal；The rigidity of spring unit is Calculated Rigidity Matrix of Bearings in step 2；
Step 3.3, main shaft load applies, and applies radial load at front-end of spindle and arranges in the speed of mainshaft and second step Preset rotation speed；Add eccentric mass at front-end of spindle, main shaft is carried out analysis of Dynamic Stiffness, obtain front-end of spindle dynamic stiffness and calculate mould Type is as follows,
K d ( ω ) = meω 2 δ ;
Wherein, m is eccentric mass, and e is the center of gravity eccentric throw relative to main shaft rotation center of eccentric mass, and ω is that main shaft turns Speed, δ is the radial displacement of front-end of spindle.
The determination method of a kind of machine tool mainshaft bearing the most according to claim 4 radially non-linear rigidity, it is characterised in that Comprising the following steps that of step 4,
According to the front-end of spindle dynamic stiffness computation model obtained in step 1 to step 3, by arranging the different speed of mainshaft and bullet The rigidity of spring unit calculates the dynamic stiffness of front-end of spindle, thus sets up the right of front-end of spindle dynamic stiffness and bearing radial rigidity Answer relational database.
The determination method of a kind of machine tool mainshaft bearing the most according to claim 4 radially non-linear rigidity, it is characterised in that Comprising the following steps that of step 5,
Use dynamic balance instrument that main shaft is carried out spot dynamic balance experiment with measuring, obtain the centroid offset of main shaft, use displacement to pass Sensor obtains the radial displacement of corresponding rotating speed lower main axis front end, obtains front-end of spindle according to front-end of spindle dynamic stiffness computation model Dynamic stiffness, is input to the dynamic stiffness obtained in the corresponding relation data base that step 4 obtains inquire about, obtains main shaft in reality The course of processing considers the radial rigidity of all bearings under each bearing loading conditions.
The determination method of a kind of machine tool mainshaft bearing the most according to claim 6 radially non-linear rigidity, it is characterised in that In step 5 during dynamic balancing measurement test, in the counterweight screws (4) that front-end of spindle installation quality is m, the center of gravity of counterweight screws (4) It is e with the eccentric throw of main shaft (1) centre of gyration；At counterweight screws (4) front plan for measuring plane, along Y in measuring plane Direction cloth displacement sensor (5), displacement transducer (5) vertical major (1) axis is the most consistent with radial direction external applied load applying direction, To measure main shaft (1) radial displacement；Choose applying external load function point in main shaft (1) front end, a bearing is installed at application point (3), bearing (3) inner ring is fixed with main shaft (1), and outer ring contacts with hydraulic cylinder (2), and hydraulic cylinder (2) applies radially external applied load, effect Force direction is Y-direction；Start main shaft (1) arranging the speed of mainshaft is ω, after main shaft (1) operating is stable, reads displacement transducer (5) registration, inputs a signal in computer (8) by signal sampler (6) and signal processing instrument (7), according to front-end of spindle Dynamic stiffness computation model obtains front-end of spindle dynamic stiffness.
CN201610560541.9A 2016-07-15 2016-07-15 A kind of determination method of machine tool mainshaft bearing radial direction non-linear rigidity Active CN106289773B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201610560541.9A CN106289773B (en) 2016-07-15 2016-07-15 A kind of determination method of machine tool mainshaft bearing radial direction non-linear rigidity

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201610560541.9A CN106289773B (en) 2016-07-15 2016-07-15 A kind of determination method of machine tool mainshaft bearing radial direction non-linear rigidity

Publications (2)

Publication Number Publication Date
CN106289773A true CN106289773A (en) 2017-01-04
CN106289773B CN106289773B (en) 2018-09-04

Family

ID=57651569

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201610560541.9A Active CN106289773B (en) 2016-07-15 2016-07-15 A kind of determination method of machine tool mainshaft bearing radial direction non-linear rigidity

Country Status (1)

Country Link
CN (1) CN106289773B (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107153734A (en) * 2017-05-09 2017-09-12 西安交通大学 The computing system and method for angular contact ball bearing non-linear rigidity under a kind of positioning pretension
CN108303251A (en) * 2018-04-19 2018-07-20 清华大学 Rigidity modeling and Indirect Detecting Method under a kind of electro spindle rotary state
CN108627309A (en) * 2018-04-19 2018-10-09 北京信息科技大学 A kind of non-linear rigidity measurement method and device for lathe
CN113239430A (en) * 2021-04-29 2021-08-10 西安交通大学 Calculation method for acting force of three-ring-plate node ring plate for power transmission steel pipe tower

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100724799B1 (en) * 2005-12-22 2007-06-04 한국항공우주연구원 Apparatus and method for bearing stiffness test
CN102201033A (en) * 2011-04-21 2011-09-28 西北工业大学 Method for analyzing dynamics of aviation multi-rotor coupling system
CN102252842A (en) * 2011-04-28 2011-11-23 湖南大学 Method and device for testing dynamic stiffness of high-speed main shaft
CN102410923A (en) * 2011-08-09 2012-04-11 西安理工大学 Rigid and non-linear relation testing device and method of cylindrical fit joint surface
CN102564763A (en) * 2011-12-22 2012-07-11 西安交通大学 Dynamic pre-tightening force measurement method of main shaft bearing of machine tool
CN103234745A (en) * 2013-05-09 2013-08-07 上海发电设备成套设计研究院 Shafting dynamic-characteristic calculation model establishment method included in spring based coupling vibration
CN103530468A (en) * 2013-10-23 2014-01-22 清华大学 Multi-support shafting finite element method with bearing stiffness coupling nonlinearity considered
CN105068504A (en) * 2015-07-31 2015-11-18 北京工业大学 Electric main shaft system modeling method taking features of combination portions into consideration

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100724799B1 (en) * 2005-12-22 2007-06-04 한국항공우주연구원 Apparatus and method for bearing stiffness test
CN102201033A (en) * 2011-04-21 2011-09-28 西北工业大学 Method for analyzing dynamics of aviation multi-rotor coupling system
CN102252842A (en) * 2011-04-28 2011-11-23 湖南大学 Method and device for testing dynamic stiffness of high-speed main shaft
CN102410923A (en) * 2011-08-09 2012-04-11 西安理工大学 Rigid and non-linear relation testing device and method of cylindrical fit joint surface
CN102564763A (en) * 2011-12-22 2012-07-11 西安交通大学 Dynamic pre-tightening force measurement method of main shaft bearing of machine tool
CN103234745A (en) * 2013-05-09 2013-08-07 上海发电设备成套设计研究院 Shafting dynamic-characteristic calculation model establishment method included in spring based coupling vibration
CN103530468A (en) * 2013-10-23 2014-01-22 清华大学 Multi-support shafting finite element method with bearing stiffness coupling nonlinearity considered
CN105068504A (en) * 2015-07-31 2015-11-18 北京工业大学 Electric main shaft system modeling method taking features of combination portions into consideration

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
田久良等: "机床主轴轴承系统热力耦合模型及其动态性能研究", 《西安交通大学学报》 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107153734A (en) * 2017-05-09 2017-09-12 西安交通大学 The computing system and method for angular contact ball bearing non-linear rigidity under a kind of positioning pretension
CN107153734B (en) * 2017-05-09 2020-05-22 西安交通大学 Computing system and method for positioning nonlinear stiffness of angular contact ball bearing under pre-tightening
CN108303251A (en) * 2018-04-19 2018-07-20 清华大学 Rigidity modeling and Indirect Detecting Method under a kind of electro spindle rotary state
CN108627309A (en) * 2018-04-19 2018-10-09 北京信息科技大学 A kind of non-linear rigidity measurement method and device for lathe
CN108627309B (en) * 2018-04-19 2021-03-23 北京信息科技大学 Nonlinear rigidity measuring method and device for machine tool
CN113239430A (en) * 2021-04-29 2021-08-10 西安交通大学 Calculation method for acting force of three-ring-plate node ring plate for power transmission steel pipe tower
CN113239430B (en) * 2021-04-29 2022-12-09 西安交通大学 Calculation method for acting force of three-ring-plate node ring plate for power transmission steel pipe tower

Also Published As

Publication number Publication date
CN106289773B (en) 2018-09-04

Similar Documents

Publication Publication Date Title
CN106289773A (en) A kind of determination method of machine tool mainshaft bearing radially non-linear rigidity
Huang et al. The application of ball-type balancers for radial vibration reduction of high-speed optic disk drives
CN106202647A (en) The Multiaxial Fatigue Life Prediction method of electro spindle and reliability estimation method fatigue life
CN106885663B (en) A kind of machine tool chief axis stiffness test method and its system
CN110020468B (en) Dynamic response analysis method for crack fault of aircraft engine wheel disc
CN105865783A (en) Method for measuring characteristics of sliding bearing film
CN107153734A (en) The computing system and method for angular contact ball bearing non-linear rigidity under a kind of positioning pretension
CN106354955A (en) Sliding bearing rigidity recognition method based on mill vibration mode parameters
CN105043737A (en) Bearing retainer trajectory measurement method based on error separation technology
CN106885662B (en) Diameter-axial composite-rotor Non-contact loader and machine tool chief axis rigidity testing system
CN106248328A (en) A kind of measurement axis architecture reverses the indirect method of dynamic flexibility
Ibraheem et al. Review of rotor balancing techniques
Zhang et al. Multiparameter modeling of piezoelectric six-degree-of-freedom accelerometer about sensitivity characteristics
CN108036906B (en) A kind of cracked rotor stiffness coefficient measurement method
CN110133103A (en) Fibre reinforced composites parameter identification method based on planar pulse sound wave exciting
Guskov et al. Experimental and numerical investigations of a dual-shaft test rig with intershaft bearing
CN106002481A (en) Testing system and method for evaluating lead screw prestretching force and dynamic performance of feeding system
CN106813816A (en) Counterweight balance is measured
Binbin et al. A double integral method for quantitative evaluation of influence on thin-walled casing response caused by bearing uncertainties
Xu et al. Effect of Detuning of Clamping Force of Tie Rods on Dynamic Performance of Rod-Fastened Jeffcott Rotor
CN109960870A (en) Multistage components Stiffness Prediction method is equipped in the large high-speed revolution surveyed and adjusted that maximized based on contact area
CN116754134A (en) Rotor imbalance state identification method based on test and simulation data fusion
Huang et al. Dynamic balance two-dimensional measuring of crankshaft assembly in motorcycle engine
Wang et al. Numerical and experimental analysis of vibration characteristics of spindle system under bearing assembly errors
Kang et al. Development and modification of a unified balancing method for unsymmetrical rotor-bearing systems

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant