CN110220706A - High-speed electric main shaft Dynamic supporting stiffness test device and test method - Google Patents
High-speed electric main shaft Dynamic supporting stiffness test device and test method Download PDFInfo
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- CN110220706A CN110220706A CN201910614445.1A CN201910614445A CN110220706A CN 110220706 A CN110220706 A CN 110220706A CN 201910614445 A CN201910614445 A CN 201910614445A CN 110220706 A CN110220706 A CN 110220706A
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- 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
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Abstract
The invention discloses a kind of high-speed electric main shaft Dynamic supporting stiffness test device and test methods, the present invention carries out contact load to loading bar by using two rolling bearings arranged side by side, load is contacted with the loading bar of front-end of spindle using housing washer, more close to electro spindle actual job operating condition, and compare non-contact load, the range of its loading force is wider, control precision is higher, it is long to continue the load time, smaller on the dynamic balancing of the loading bar of electro spindle output end influence, measurable experiment revolving speed is higher；Measurement can be synchronized to loading force and displacement deformation by sensor simultaneously, accurately can measure and calculate the Dynamic supporting stiffness of electro spindle.
Description
Technical field
The present invention relates to a kind of high-speed electric main shaft Dynamic supporting stiffness test device and test methods.
Background technique
High-speed electric main shaft directly influences the machining accuracy and production of lathe as the core component in high-speed processing machine tool
Efficiency.With to the big output power of high-speed electric main shaft and it is high-revolving increasingly pursue, need the Dynamic supporting stiffness of main shaft bearing
Increasing, this becomes the emphasis of designer's care.But due to high-speed electric main shaft design feature and applying working condition, to its into
The test of Mobile state support stiffness always is difficult point.The existing experimental study to electro spindle Dynamic supporting stiffness is simultaneously few, mainly
Include: contact load measurement Dynamic supporting stiffness, for example uses piezoelectric ceramics or hydraulic cylinder as actuator to load cover master
The method of housing washer on axis rotor, but this mode is affected to the dynamic balancing of rotor due to rolling bearing, with
And the abrasion and temperature rise of rolling bearing are larger, which is only suitable for the dynamic rate test of low speed.Non-contact load measurement dynamic
Support stiffness, for example load, but non-contact load pair are realized in the way of electromagnetic exciter, electromagnet load and static air pressure etc.
Structure design, machining accuracy and installation accuracy propose harsh requirement, meanwhile, loading force is smaller, and loading force is not easy accurately
The defects of control and measurement.In conclusion for the key of high-speed electric main shaft dynamic support stiffness measurement being realized to its dynamic
All there is respective defect, it is rigid to its dynamic to be unable to satisfy modern industry in load, the above contact load and non-contact loading method
The eager demand of degree.
Summary of the invention
The object of the present invention is to provide a kind of high-speed electric main shaft Dynamic supporting stiffness test device and test methods, pass through one
Simple, the easy to operate experimental provision of kind structure, can accurately measure electro spindle Dynamic supporting stiffness, be electro spindle
Dynamic property research and quality testing provide experiment basis.
In order to solve the above technical problems, the present invention provides a kind of high-speed electric main shaft Dynamic supporting stiffness test device, including
For applying the machinery loading device of radial loaded power to the loading bar of electro spindle output end, adding for controlling machinery loading device
Carry the add load control of power and the data acquisition unit of the change in displacement for acquiring the loading force and loading bar；Institute
Stating mechanical airborne device includes rigidity pedestal, is set at the top of the rigidity pedestal there are two rolling bearing arranged side by side, is rolled
The outer ring of bearing contacts load with loading bar；The add load control includes that the power dress of active force is provided to rigidity pedestal
It sets.
Further, which further includes lubricating arrangement, and the lubricating arrangement includes lubrication conduit, and the lubrication is led
One end of pipe is connect with lubricant reservoir case, and the nozzle of the other end, which is met to the load(ing) point of loading bar, to be arranged, for mentioning to load(ing) point
For lubricant.
Further, the data acquisition unit includes the active force applied for measuring power device to rigidity pedestal
Pressure sensor, the surface that the load(ing) point of loading bar is arranged in are used to detect displacement of the loading bar under loading force effect
Current vortex sensor.
Further, the rigidity pedestal is fixed on the rack by sliding pair, and the sliding pair includes being fixed on rack
On glide base and through the glide base and the slipping column that is slidably connected with the glide base, the support
One end is connect with the rigidity pedestal, and the other end is connect with the output end of the power device；The pressure sensor setting exists
Between the output end and slipping column of power device.
Further, which further includes the power device installing mechanism for adjusting power device position, described
Power device installing mechanism includes the first column, the first sleeve being arranged on first column and horizontally disposed and with the
The mounting plate that the tube wall of sleeve is fixedly connected, the first sleeve can be slided up and down along the first column, the power device peace
On the mounting plate.
Further, the power device includes cylinder and the electricity for connecting and be used to control cylinder operation with the cylinder
Gas proportioning valve, the pressure sensor are arranged between the piston rod of cylinder and slipping column.
Further, the piston rod of the cylinder is connected by floating junction with the jointing of pressure sensor.
In addition, the present invention also provides a kind of test sides of above-mentioned measuring device measurement high-speed electric main shaft Dynamic supporting stiffness
Method, comprising the following steps:
S1: radial loaded power suffered by the loading bar of acquisition electro spindle output end and loading bar are in the radial loaded power
Displacement under effect；
S2: establishing the equivalent model of electro spindle, and determines according to the equivalent model support of the front/rear bearing of electro spindle
Point；
S3: the load of the supporting point of the front/rear bearing of electro spindle is calculated according to statics balance condition, is existed according to loading bar
The displacement of the supporting point of the front/rear bearing of displacement calculation electro spindle under the effect of radial loaded power, it is finally rigid according to bearing
The dynamic radial support stiffness for the front/rear bearing that electro spindle is calculated in degree definition is electro spindle Dynamic supporting stiffness.
Further, the step S2 is specifically included:
S21: being considered as a set of double-row bearing for the front and back bearings of electro spindle, establishes the equivalent model of electro spindle, determines radial
Load FrUseful effect point D；
S22: according to the distance between former and later two two-row ball bearing Centers of Pressure laGreater than two in single double-row bearing
The distance between a bearing pressure center lbWhen, FrThe movement of position can be ignored, by the supporting-point of the front/rear bearing of electro spindle
It is reduced to the midpoint A point and B point of respective two bearing pressure lines of centres.
Further, the step S3 is specifically included:
S31: specific used by calculating the load of the supporting point of the front/rear bearing of electro spindle according to statics balance condition
Formula are as follows:
Wherein: lijFor the horizontal distance between equivalent point each in equivalent model, FAFor the load of the supporting point A of the fore bearing of main shaft
Lotus, FBFor the load of the supporting point B of the rear bearing of main shaft,
S32: according to the supporting point A's of the fore bearing of displacement calculation electro spindle of the loading bar under the effect of radial loaded power
Used by the displacement of displacement and the supporting point B of rear bearing method particularly includes:
According to the equivalent model of electro spindle:
yC=y1+y3 (3)
yE=y2+y4 (4)
Wherein, yCFor collected displacement at loading bar displacement collection point C, yEAt loading bar displacement collection point E
Collected displacement；y1And y2The bearing for respectively assuming electro spindle is rigidity, loading bar displacement when no radial displacement deforms
The displacement of collection point C and loading bar displacement collection point E；y3And y4The support shaft for respectively assuming electro spindle is rigidity, no diameter
The displacement of loading bar displacement collection point C and loading bar displacement collection point E when to displacement deformation；
According to Analysis of materials mechanics electro spindle rotor in external force FrSag curve under effect can obtain:
Wherein: E is the elasticity modulus of rotor；J is the equivalenting inertia torque of rotor,dvFor rotor
Equivalent diameter,diFor the diameter of i-th section of multi-diameter shaft, liFor the length of i-th section of multi-diameter shaft, L is ladder
The total length of axis, N are the shaft end number of multi-diameter shaft.
It can be obtained by the geometrical relationship of electro spindle deformation displacement:
Wherein, δAAnd δBThe respectively position of the supporting point B of the displacement and rear bearing of the supporting point A of the fore bearing of electro spindle
Shifting amount；
S32: the dynamic radial support stiffness K that the fore bearing of electro spindle is calculated is defined according to bearing rigidityAAnd rear axle
The dynamic radial support stiffness K heldBUsed specific formula are as follows:
Add the invention has the benefit that carrying out contact to loading bar by using two rolling bearings arranged side by side
It carries, so that the range of loading force is extensively high with control precision, smaller, measurable experiment is influenced on the dynamic balancing of the rotor of electro spindle
Revolving speed is higher；Measurement can be synchronized to loading force and displacement deformation simultaneously, it can be achieved that accurate measurement is in order to calculate
The Dynamic supporting stiffness of electro spindle；In addition, the test device is lower to installation accuracy requirement；Structure is simple, easy to operate, and is
Unification and independence are vertical, can load to a variety of electro spindles, versatility is good.
Detailed description of the invention
The drawings described herein are used to provide a further understanding of the present application, constitutes part of this application, at this
The same or similar part, the illustrative embodiments and their description of the application are indicated using identical reference label in a little attached drawings
For explaining the application, do not constitute an undue limitation on the present application.In the accompanying drawings:
Fig. 1 is the composition block diagram of one embodiment of the invention；
Fig. 2 is the structural schematic diagram of one embodiment of the invention；
Fig. 3 is the loading principle figure of one embodiment of the invention；
Fig. 4 is the A-A cross-sectional view of Fig. 3；
Fig. 5 is the equivalent model of the high-speed electric main shaft of one embodiment of the invention.
Wherein: 1, rigidity pedestal；11, Base body；12, the first groove；13, the second groove；14, flange connector；15, solid
Determine hole；2, rolling bearing；21, shaft；22, nut；3, slipping column；31, glide base；32, cylinder；33, floating junction；
34, electric Proportion valve；4, pressure sensor；5, the first column；51, mounting plate；6, electro spindle；7, current vortex sensor；71,
Two columns；72, the second casing；73, fixed plate；74, mounting base；8, lubrication conduit；81, catheter holder；82, lubricant reservoir
Case；9, rack；10, loading bar.
Specific embodiment
High-speed electric main shaft Dynamic supporting stiffness test device as depicted in figs. 1 and 2, including be used for electro spindle output end
Loading bar 10 apply radial loaded power machinery loading device, for control machinery loading device loading force load control dress
It sets and the data acquisition unit of the change in displacement for acquiring the loading force and loading bar 10；The machinery airborne device
Including rigidity pedestal 1, the top of the rigidity pedestal 1 sets that there are two rolling bearing 2 arranged side by side, the outer rings of rolling bearing 2
Load is contacted with loading bar 10；The add load control includes providing the power device of active force to rigidity pedestal 1.Such as Fig. 3
With shown in Fig. 4, the top of rigidity pedestal 1 opens up that there are two 12 and second groove 13 in decussation, two rolling bearings
2 are mounted in the second groove 13 by shaft 21, and are locked by nut 22, and described 12 are located at the center of two rolling bearings 2
Between；When load, loading bar 10 is adjusted between two rolling bearings 2, the outer ring of rolling bearing 2 is contacted with loading bar 10 and adds
It carries.
The application carries out contact load to loading bar 10 by using two rolling bearings 2 arranged side by side, using rolling
2 outer ring of bearing contacts load with the loading bar 10 of front-end of spindle, more close to 6 actual job operating condition of electro spindle, and compared to non-
Contact load, the range of loading force is wider, control precision higher, the lasting load time is long, the load to electro spindle output end
The dynamic balancing influence of stick 10 is smaller, and measurable experiment revolving speed is higher；Loading force and displacement can be become by sensor simultaneously
Shape synchronizes measurement, accurately can measure and calculate the Dynamic supporting stiffness of electro spindle 6.
According to one embodiment of the application, which further includes lubricating arrangement, and the lubricating arrangement includes lubrication
One end of conduit 8, the lubrication conduit 8 connect 82 with lubricant reservoir case, and the nozzle of the other end meets the load to loading bar 10
Point setting, for providing lubricant to load(ing) point, oil duct 8 is fixed in rack 9 by catheter holder 81.It is specific when experiment
The mode butt contact that oil-air lubrication can be used is cooled down and is lubricated, and changing conventional contacts load can only be to static state and low turn
Under speed the shortcomings that test, the maximum speed for further increasing experiment measurement can be conducive to.
According to one embodiment of the application, the data acquisition unit includes for measuring power device to rigidity pedestal
The pressure sensor 4 of 1 active force applied, the surface that the load(ing) point of loading bar 10 is arranged in are adding for detecting loading bar 10
Carry the current vortex sensor 7 of the displacement under power effect.Two current vortex sensors 7 can be used in experimentation to be fixed by bracket
Two measurement points chosen near the surface in contact loading position measure the displacement deformation of loading bar 10 in loading procedure
Amount, to improve the accuracy of measurement data；The bracket includes the second column 71 being fixed in rack 9, setting described the
The second casing 72 on two columns 71 and the mounting base 74 being fixedly connected with the tube wall of first sleeve, the mounting base 74 are in L
Type, the vertical component effect of mounting base 74 are fixedly connected with the tube wall of first sleeve, and current vortex sensor 7 is mounted on the level of mounting base 74
Portion.Measurement is synchronized to loading force and displacement deformation by pressure sensor 4 and current vortex sensor 7, using a bar Waters
Low-pass filter, then carry out curve fitting, the relationship of loading force and vibration displacement is obtained, is obtained finally by empirical theory formula
The Dynamic supporting stiffness of electro spindle 6, it can be achieved that the Dynamic supporting stiffness of electro spindle 6 survey calculation.
According to one embodiment of the application, the rigidity pedestal 1 is fixed in rack 9 by sliding pair, the sliding
Pair includes the glide base 31 being fixed in rack 9 and slides company through the glide base 31 and with the glide base 31
The slipping column 3 connect, one end of the support are connect with the rigidity pedestal 1, the output end of the other end and the power device
Connection；The pressure sensor 4 is arranged between the output end of power device and slipping column 3.Slipping column 3 and it is fixed on reality
The glide base 31 tested on platform constitutes sliding pair, pushes slipping column 3 to move up by power device, so that being mounted on sliding
2 outer ring of rolling bearing on pillar 3 contacts realization load with 6 rotor of electro spindle.The bottom of rigidity pedestal 1 and slipping column 3
Top be equipped with and scheme flange connector 14 out outward, flange connector is equipped with fixation hole 15, and two flange connectors pass through fastening
Part fixation is detachably connected.
According to one embodiment of the application, which further includes the power device for adjusting power device position
Installing mechanism, the power device installing mechanism include the first column 5, the first sleeve being arranged on first column 5 with
And mounting plate 51 that is horizontally disposed and being fixedly connected with the tube wall of first sleeve, the first sleeve can be along the first about 5 column
Sliding, the power device are mounted on the mounting plate 51.The power device installing mechanism is two-freedom regulating mechanism, high
The adjustability of degree effectively shortens the stroke of cylinder 32, and increases the effective travel of load,
According to one embodiment of the application, the power device includes that cylinder 32 and connecting with the cylinder 32 is used in combination
In the electric Proportion valve 34 that control cylinder 32 works, the piston rod and slipping column 3 of cylinder 32 is arranged in the pressure sensor 4
Between.The input voltage of electric Proportion valve 34 is adjusted by data acquisition software, just 32 admission pressure of adjustable cylinder is to control
The variation of loading force processed, electric Proportion valve 34, which realizes, accurately controls 32 admission pressure of cylinder, to realize to load
The accurate control of power.It can also be measured by revolving speed of the velocity sensor to electro spindle in experimentation.
According to one embodiment of the application, the piston rod of the cylinder 32 passes through floating junction 33 and pressure sensor 4
Jointing be connected, floating junction 33 can effectively subtract for adjusting due to manufacturing and installing caused coaxiality error
Small part mismachining tolerance and installation error bring influence.
In addition, the present invention also provides a kind of tests of above-mentioned measuring device measurement 6 Dynamic supporting stiffness of high-speed electric main shaft
Method, comprising the following steps:
S1: radial loaded power suffered by the loading bar 10 of acquisition electro spindle output end and loading bar 10 add in the radial direction
Carry the displacement under power effect；
S2: the equivalent model (as shown in Figure 5) of electro spindle 6 is established, and electro spindle 6 is determined according to the equivalent model
The supporting point of front/rear bearing；
S3: the load of the supporting point of the front/rear bearing of electro spindle 6 is calculated according to statics balance condition, according to loading bar
The displacement of the supporting point of the front/rear bearing of the 10 displacement calculation electro spindle 6 under the effect of radial loaded power, finally according to axis
Hold rigidity and define that the dynamic radial support stiffness of the front/rear bearing of electro spindle 6 is calculated is that 6 dynamic support of electro spindle is rigid
Degree.
According to one embodiment of the application, the step S2 is specifically included:
The front and back bearings of experiment electro spindle 6 can be considered a set of double-row bearing, analyze the radial load F of double-row bearingrWhen, it needs
First to determine radial load FrUseful effect point.If axial load FaIt is 0, radial load FrAct on the pressure of double-row bearing
Power center.If axial load FaIt is not 0, radial load FrUseful effect point will to bear axial load that column roll
The Center of Pressure of body is mobile.But as the distance between former and later two two-row ball bearing Centers of Pressure laGreater than in single double-row bearing
The distance between two bearing pressure centers lbWhen (as shown in Figure 5), FrThe movement of position can be ignored.6 bearing of electro spindle
Supporting structure meets above-mentioned condition, therefore the supporting-point for testing the front/rear bearing of electro spindle 6 is all reduced to respective two bearing pressures
The midpoint A point and B point of the line of centres.Radial point of force application is named as D point, the load of two current vortex sensors 7 measurement
The position of 10 displacement deformation of stick is named as C point and E point.
According to one embodiment of the application, the step S3 is specifically included:
It is specific public used by calculating the load of the supporting point of the front/rear bearing of electro spindle 6 according to statics balance condition
Formula are as follows:
Wherein: lijFor the horizontal distance between equivalent point each in equivalent model, FAFor the load of the supporting point A of the fore bearing of main shaft
Lotus, FBFor the load of the supporting point B of the rear bearing of main shaft,
According to the supporting point A's of the fore bearing of displacement calculation electro spindle 6 of the loading bar 10 under the effect of radial loaded power
Used by the displacement of displacement and the supporting point B of rear bearing method particularly includes:
According to the equivalent model of electro spindle 6:
yC=y1+y3 (3)
yE=y2+y4 (4)
Wherein, yCFor collected displacement at 10 displacement collection point C of loading bar, yEFor the acquisition of 10 displacement of loading bar
Collected displacement at point E；y1And y2The bearing for respectively assuming electro spindle 6 is rigidity, loading bar when no radial displacement deforms
The displacement of 10 displacement collection point E of 10 displacement collection point C and loading bar；y3And y4Respectively assume the support shaft of electro spindle 6
For rigidity, the displacement of 10 displacement collection point E of 10 displacement collection point C of loading bar and loading bar when no radial displacement deforms；
According to 6 rotor of Analysis of materials mechanics electro spindle in external force FrSag curve under effect can obtain:
Wherein: E is the elasticity modulus of rotor；J is the equivalenting inertia torque of rotor,dvFor rotor
Equivalent diameter,diFor the diameter of i-th section of multi-diameter shaft, liFor the length of i-th section of multi-diameter shaft, L is ladder
The total length of axis, N are the shaft end number of multi-diameter shaft.
It can be obtained by the geometrical relationship of 6 deformation displacement of electro spindle:
Wherein, δAAnd δBThe respectively position of the supporting point B of the displacement and rear bearing of the supporting point A of the fore bearing of electro spindle 6
Shifting amount；
The dynamic radial support stiffness K that the fore bearing of electro spindle 6 is calculated is defined according to bearing rigidityAWith rear bearing
Dynamic radial support stiffness KBUsed specific formula are as follows:
The radial loaded power F of point A He point B can be calculated by formula (1) and formula (2)AAnd FB, joint type (3)~formula (6) can count
Calculate y3And y4, and substituted into formula (9) and formula (10) can Simultaneous Equations solution point A and point B radial-deformation δAWith
δB；Finally by δAAnd δBThe dynamic radial support stiffness that substitution formula (9) and formula (10) can acquire the front/rear bearing of electro spindle 6 is completed
Measurement.
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 technical solution of the present invention, should all be covered at this
In the scope of the claims of invention.
Claims (10)
1. a kind of high-speed electric main shaft Dynamic supporting stiffness test device, which is characterized in that including for electro spindle output end
Loading bar apply radial loaded power machinery loading device, for control the add load control of machinery loading device loading force with
And the data acquisition unit of the change in displacement for acquiring the loading force and loading bar；The machinery airborne device includes rigid
Pedestal is spent, is set at the top of the rigidity pedestal there are two rolling bearing arranged side by side, outer ring and the loading bar of rolling bearing connect
Touching load；The add load control includes providing the power device of active force to rigidity pedestal.
2. high-speed electric main shaft Dynamic supporting stiffness test device according to claim 1, which is characterized in that the test device
It further include lubricating arrangement, the lubricating arrangement includes lubrication conduit, and one end of the lubrication conduit is connect with lubricant reservoir case,
The nozzle of the other end, which is met to the load(ing) point of loading bar, to be arranged, for providing lubricant to load(ing) point.
3. high-speed electric main shaft Dynamic supporting stiffness test device according to claim 1, which is characterized in that the data are adopted
Collection unit includes the pressure sensor for measuring the active force that power device applies to rigidity pedestal, and adding for loading bar is arranged in
The surface of loading point is used to detect the current vortex sensor of displacement of the loading bar under loading force effect.
4. the high-speed electric main shaft Dynamic supporting stiffness test device stated according to claim 3, which is characterized in that the rigidity pedestal
It is fixed on the rack by sliding pair, the sliding pair includes the glide base being fixed on the rack and through the sliding base
Seat and the slipping column that is slidably connected with the glide base, one end of the support are connect with the rigidity pedestal, the other end
It is connect with the output end of the power device；The pressure sensor be arranged in power device output end and slipping column it
Between.
5. high-speed electric main shaft Dynamic supporting stiffness test device according to claim 1, which is characterized in that the test device
It further include the power device installing mechanism for adjusting power device position, the power device installing mechanism includes first vertical
Column, the first sleeve being arranged on first column and installation that is horizontally disposed and being fixedly connected with the tube wall of first sleeve
Plate, the first sleeve can be slided up and down along the first column, and the power device is mounted on the mounting plate.
6. high-speed electric main shaft Dynamic supporting stiffness test device according to claim 4, which is characterized in that the power dress
Set including cylinder and connect with the cylinder and be used to control the electric Proportion valve of cylinder operation, the pressure sensor setting
Between the piston rod and slipping column of cylinder.
7. high-speed electric main shaft Dynamic supporting stiffness test device according to claim 6, which is characterized in that the cylinder
Piston rod is connected by floating junction with the jointing of pressure sensor.
8. a kind of test side using any measuring device measurement high-speed electric main shaft Dynamic supporting stiffness of claims 1-7
Method, which comprises the following steps:
S1: radial loaded power suffered by the loading bar of acquisition electro spindle output end and loading bar are acted in the radial loaded power
Under displacement；
S2: establishing the equivalent model of electro spindle, and determines according to the equivalent model supporting point of the front/rear bearing of electro spindle；
S3: the load of the supporting point of the front/rear bearing of electro spindle is calculated according to statics balance condition, according to loading bar in radial direction
The displacement of the supporting point of the front/rear bearing of displacement calculation electro spindle under loading force effect, it is finally fixed according to bearing rigidity
The dynamic radial support stiffness that the front/rear bearing of electro spindle is calculated in justice is electro spindle Dynamic supporting stiffness.
9. high-speed electric main shaft Dynamic supporting stiffness test method according to claim 8, which is characterized in that the step S2
It specifically includes:
S21: the front and back bearings of electro spindle are considered as a set of double-row bearing, establish the equivalent model of electro spindle, determine radial load Fr
Useful effect point D；
S22: according to the distance between former and later two two-row ball bearing Centers of Pressure laGreater than two bearings in single double-row bearing
The distance between Center of Pressure lbWhen, FrThe movement of position can be ignored, and the supporting-point of the front/rear bearing of electro spindle is reduced to
The midpoint A point and B point of respective two bearing pressure lines of centres.
10. high-speed electric main shaft Dynamic supporting stiffness test method according to claim 9, which is characterized in that the step
S3 is specifically included:
S31: specific formula used by calculating the load of the supporting point of the front/rear bearing of electro spindle according to statics balance condition
Are as follows:
Wherein: lijFor the horizontal distance between equivalent point each in equivalent model, FAFor the load of the supporting point A of the fore bearing of main shaft, FB
For the load of the supporting point B of the rear bearing of main shaft,
S32: according to the displacement of the supporting point A of the fore bearing of displacement calculation electro spindle of the loading bar under the effect of radial loaded power
Used by the displacement of the supporting point B of amount and rear bearing method particularly includes:
According to the equivalent model of electro spindle:
yC=y1+y3 (3)
yE=y2+y4 (4)
Wherein, yCFor collected displacement at loading bar displacement collection point C, yETo be acquired at loading bar displacement collection point E
The displacement arrived；y1And y2The bearing for respectively assuming electro spindle is rigidity, and loading bar displacement acquires when no radial displacement deforms
The displacement of point C and loading bar displacement collection point E；y3And y4The support shaft for respectively assuming electro spindle is rigidity, without radial position
The displacement of loading bar displacement collection point C and loading bar displacement collection point E when moving deformation；
According to Analysis of materials mechanics electro spindle rotor in external force FrSag curve under effect can obtain:
Wherein: E is the elasticity modulus of rotor；J is the equivalenting inertia torque of rotor,dvIt is straight for the equivalent of rotor
Diameter,diFor the diameter of i-th section of multi-diameter shaft, liFor the length of i-th section of multi-diameter shaft, L is the total of multi-diameter shaft
Length, N are the shaft end number of multi-diameter shaft.
It can be obtained by the geometrical relationship of electro spindle deformation displacement:
Wherein, δAAnd δBThe respectively displacement of the supporting point B of the displacement and rear bearing of the supporting point A of the fore bearing of electro spindle；
S32: the dynamic radial support stiffness K that the fore bearing of electro spindle is calculated is defined according to bearing rigidityAWith moving for rear bearing
State radial support stiffness KBUsed specific formula are as follows:
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| CN114799107A (en) * | 2022-04-14 | 2022-07-29 | 河钢乐亭钢铁有限公司 | Pull rod compensation control method for improving accuracy of roll gap of fan-shaped section |
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| CN110220706B (en) | 2020-10-13 |
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