CN106768749A - A kind of main shaft bearing joint portion device for testing dynamic stiffness - Google Patents
A kind of main shaft bearing joint portion device for testing dynamic stiffness Download PDFInfo
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- CN106768749A CN106768749A CN201710092626.3A CN201710092626A CN106768749A CN 106768749 A CN106768749 A CN 106768749A CN 201710092626 A CN201710092626 A CN 201710092626A CN 106768749 A CN106768749 A CN 106768749A
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- bearing
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- power transmission
- joint portion
- dynamic stiffness
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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
- G01M5/00—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings
- G01M5/0041—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings by determining deflection or stress
- G01M5/005—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings by determining deflection or stress by means of external apparatus, e.g. test benches or portable test systems
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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
- G01M13/04—Bearings
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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
- G01M13/04—Bearings
- G01M13/045—Acoustic or vibration analysis
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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
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
- G01M7/02—Vibration-testing by means of a shake table
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- General Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Engineering & Computer Science (AREA)
- Aviation & Aerospace Engineering (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
Dynamic characteristic parameter technical field of measurement and test the present invention relates to bearing under different operating loadings, more particularly to a kind of main shaft bearing joint portion device for testing dynamic stiffness.Including base plate and the electric machine assembly being arranged on base plate, speed probe, accelerator, spring bearing component, bearing assembly to be measured, exciting device, power transmission shaft, shaft position sensor and radial displacement transducer, bearing assembly wherein to be measured and exciting device are sheathed on power transmission shaft, the two ends of power transmission shaft are connected with accelerator and electric machine assembly successively by spring bearing modular support and one end, and speed probe, shaft position sensor and radial displacement transducer are respectively used to measure rotating speed, axial displacement and the radial displacement of power transmission shaft.It is present invention measurement convenience, clear in structure, simple to operate, actual condition can be imitated and measure bearing rigidity, research bearing combining part dynamic characteristic and the rational pretightning force of determination are played an important role.
Description
Technical field
Dynamic characteristic parameter technical field of measurement and test the present invention relates to bearing under different operating loadings, it is more particularly to a kind of
Main shaft bearing joint portion device for testing dynamic stiffness.
Background technology
Angular contact ball bearing is one of application in machine equipments part widely, and its rigidity property directly influences master
The stiffness characteristics of axle system, particularly in the case of running at high speed, the rigidity of angular contact ball bearing directly affects axis system
Dynamic characteristic, and then the machining accuracy of lathe is influenceed, thus the rigidity of angular contact ball bearing is studied, particularly dynamic stiffness has non-
Often important meaning.
Early in eighties of last century mid-term, the researcher of the former Soviet Union enters to the joint portion vibration problem for influenceing machine finish
Research is gone.To 70 to the eighties in last century, it is this with regard to bearing that the related researcher of Britain is based on Hertzian contact theory
Theory deduction research has been carried out in common joint portion, and devises small-sized testing stand and demonstrate experience by regression analysis and calculate
The correctness of formula.But due to the backwardness of computer level at that time so that the solution of bearing dynamic stiffness needs to expend substantial amounts of
Time.To 20 th century laters, there is a growing awareness that shadow of the dynamic property of joint portion to heave-load device machining accuracy
Ring, people have carried out substantial amounts of experiment test work, the rigidity, damping, modal frequency and life-span including bearing etc. have accumulated big
The experimental data of amount.To 21 century, with developing rapidly for electronic computer technology, researcher starts using based on hertz
The accurate calculating of the accurate iterative algorithm of contact theory and many geometrical factors of consideration to carry out joint portion rigidity is studied.
At present, in the problem of research bearing rigidity, including the Static stiffness and dynamic stiffness for studying bearing.Both of which is reflected
The ability of structure resistance to deformation, difference is the energy that Static stiffness refers to bearing resistance static displacement change during steady load
Power；And dynamic stiffness is when referring to bearing alternation dynamic loading, the ability of resistance dynamic displacement change, dynamic stiffness is to weigh structure antivibration
The leading indicator of ability, thus the test of research bearing dynamic stiffness to it is accurate obtain spindle bearing system dynamics have it is important
Meaning.
The test device of test bearing joint portion dynamic stiffness is less, and most test objects are obtained just for single bearing
Different bearing dynamic characteristic parameters are significant under taking different operating modes.
The content of the invention
Regarding to the issue above, it is an object of the invention to provide a kind of main shaft bearing joint portion device for testing dynamic stiffness, this
Device to test high precision can simultaneously measure different bearings axially and radial dynamical characteristic parameter.
To achieve these goals, the present invention uses following technical scheme：
A kind of main shaft bearing joint portion device for testing dynamic stiffness, including base plate and be arranged on base plate electric machine assembly, turn
Fast sensor, accelerator, spring bearing component, bearing assembly to be measured, power transmission shaft and shaft position sensor, wherein bearing to be measured
Assembly set on the power transmission shaft, the two ends of the power transmission shaft by spring bearing modular support and one end successively with acceleration
Device and electric machine assembly are connected, the speed probe and shaft position sensor be respectively used to measure the power transmission shaft rotating speed and
Axial displacement.
The bearing assembly to be measured includes pre-load nut, thrust ball bearing, pretension force loading device, bearing block, bearing block
Support, measured bearing and bearing (ball) cover, wherein bearing bracket are arranged on the base plate, the bearing block and bearing bracket
Connection, the pretension force loading device is arranged in the bearing block and can axially move, the pre-load nut and the axle
The threaded one end of bearing is connected and is connected with pretension force loading device by thrust ball bearing, and the measured bearing is arranged at institute
State the other end and the bearing (ball) cover axial limiting by being connected with bearing block of bearing block.
End ring is provided between the pretension force loading device and measured bearing.
The pretension force loading device includes outer back-up ring, spring support, spring, fixes sleeve and inner shield ring, and its China and foreign countries keeps off
Multiple spring supports with diameter parallel are connected between circle and inner shield ring, one end of each spring support is fixed with inner shield ring and connected
Connect, the other end is slidably connected with the outer back-up ring, spring is arranged with each spring support, the fixes sleeve is sheathed on described
The outside of outer back-up ring and inner shield ring.
Be provided with chute on the side wall of described fixes sleeve vertically, the outer back-up ring and inner shield ring respectively by screw with
The slide connection.
The power transmission shaft is provided with multidiameter structure, and multiple measured bearings can be installed in the multidiameter structure.
The speed probe by speed probe support be arranged on base plate on and with the output shaft of the electric machine assembly
It is corresponding；The shaft position sensor by shaft position sensor support be arranged on base plate on and with the power transmission shaft
End is corresponding.
The test device further includes exciting device and radial displacement transducer, and the exciting device is sheathed on described
On power transmission shaft, the radial displacement transducer is arranged between the exciting device and the bearing assembly to be measured.
The exciting device includes exciting disk and eccentric massblock, and wherein exciting disk is fixed on power transmission shaft, the exciting
Multiple through holes are evenly equipped with disk, the eccentric massblock is fixed on the through hole on exciting disk.
The radial displacement transducer is arranged on base plate by radial displacement transducer support.
Advantages of the present invention is with beneficial effect：
1. the present invention can provide proper axial pretightning force using pretension force loading device and the exciting disk with eccentric mass,
With different radial loads, the influence of different pretightning forces and different radial loads to bearing dynamic stiffness can be measured；
2. multidiameter structure of the invention can conveniently install various different model bearings, there is certain interchangeability, save system
Cause this；
3. the present invention greatly reduces the complexity of test, simple to operate, easily accurately obtains bearing dynamic characteristic
Test signal；
4. when the present invention is axially or radially encouraged to test device, bearing dynamic characteristic parameter can be obtained accurately,
Reasonable Parameters are provided to obtain bearing dynamic characteristic；
5. when the present invention is calculated, drive shaft displacement is eliminated, measurement model result is more met reality, test knot
Fruit is more accurate；
6. different model bearing engagement surface dynamic characteristic parameter can be obtained using the device, so as to set up Contact characteristics
Data in database are further fitted by parameter database, for select reasonable pretightning force and bearing pairing mode provide data according to
According to.
Brief description of the drawings
Fig. 1 is structural representation of the invention；
Fig. 2 is the structural representation of bearing assembly to be measured in the present invention；
Fig. 3 is the axonometric drawing of bearing assembly to be measured in the present invention；
Fig. 4 is the explosive view of bearing assembly to be measured in the present invention；
Fig. 5 is the axonometric drawing of pretension force loading device in the present invention；
Fig. 6 is the axonometric drawing of pretension force loading device in the present invention；
Fig. 7 is the explosive view of pretension force loading device in the present invention；
Fig. 8 is the structural representation of exciting disk in the present invention；
Fig. 9 is the structural representation of power transmission shaft in the present invention；
Figure 10 is experimental provision principle schematic of the invention.
In figure：1 is base plate, and 2 is electric machine assembly, and 3 is speed probe support, and 4 is speed probe, and 5 is accelerator, 6
It is shaft coupling, 7 is the first spring bearing component, and 8 is bearing assembly to be measured, and 9 is radial displacement transducer support, and 10 is radial direction position
Displacement sensor, 11 is exciting disk, and 12 is eccentric massblock, and 13 is power transmission shaft, and 14 is shaft position sensor, and 15 is axial displacement
Sensor stand, 16 is pre-load nut, and 17 is thrust ball bearing, and 18 is pretension force loading device, and 19 is bearing block, and 20 is bearing
Seat support, 21 is end ring, and 22 is measured bearing, and 23 is bearing (ball) cover, and 24 is outer back-up ring, and 25 is spring support, and 26 is bullet
Spring, 27 is fixes sleeve, and 28 is inner shield ring, and 29 is chute, and 30 is multidiameter structure.
Specific embodiment
In order that the object, technical solutions and advantages of the present invention are clearer, below in conjunction with the accompanying drawings with specific embodiment pair
The present invention is described in detail.
As shown in figure 1, the present invention provides a kind of bearing combining part device for testing dynamic stiffness, including the base plate 1 and bottom of installed in
Electric machine assembly 2, speed probe 4 in the T-slot of plate 1, accelerator 5, spring bearing component, bearing assembly to be measured 8, power transmission shaft
13 and shaft position sensor 14, wherein bearing assembly to be measured 8 is sheathed on power transmission shaft 13, the two ends of power transmission shaft 13 are by support
Bearing assembly is supported and one end is connected with accelerator 5 and electric machine assembly 2 successively, speed probe 4 and shaft position sensor 14
It is respectively used to measure the rotating speed and axial displacement of power transmission shaft 13.
Speed probe 4 is arranged on base plate 1 and relative with the output shaft of electric machine assembly 2 by speed probe support 3
Should；Shaft position sensor 14 by shaft position sensor support 15 be arranged on base plate 1 on and with the end phase of power transmission shaft 13
Correspondence.
As in Figure 2-4, bearing assembly to be measured 8 includes pre-load nut 16, thrust ball bearing 17, pretension force loading device
18th, bearing block 19, bearing bracket 20, measured bearing 22 and bearing (ball) cover 23, wherein bearing bracket 20 are arranged on base plate 1
On, bearing block 19 and bearing bracket 20 are connected, and pretension force loading device 18 is arranged in bearing block 19 and can move vertically
Dynamic, pre-load nut 16 is connected with the threaded one end of bearing block 19 and is connected with pretension force loading device 18 by thrust ball bearing 17
Connect, measured bearing 22 is arranged at the other end of bearing block 19 and the bearing (ball) cover 23 by being connected with bearing block 19 is axially limited
Position.End ring 21 is provided between pretension force loading device 18 and measured bearing 22.
As illustrated in figs. 5-7, pretension force loading device 18 includes outer back-up ring 24, spring support 25, spring 26, fixes sleeve 27
And inner shield ring 28, multiple spring supports 25 with diameter parallel, each spring are connected between its China and foreign countries' back-up ring 24 and inner shield ring 28
One end of support 25 is fixedly connected with inner shield ring 28, and the other end is slidably connected with outer back-up ring 24, is arranged on each spring support 25
There is spring 26, fixes sleeve 27 is sheathed on the outside of outer back-up ring 24 and inner shield ring 28.
Chute 29 is provided with the side wall of fixes sleeve 27 vertically, outer back-up ring 24 and inner shield ring 28 pass through screw and cunning respectively
Groove 29 is slidably connected.Spring 26 can provide different pretightning forces under being in different compressive states, and fixes sleeve 27 can prevent outer
Back-up ring 24 and inner shield ring 28 relatively rotate.
Further, the end of the outer back-up ring 24 in pre-load nut 16 and pretension force loading device 18 has boss to prop up jointly
Support thrust ball bearing 17, by non-threaded portion sub-support in bearing block 19, end ring 21 is placed on pre- pretension force loading device 18
Between clamp force loading device 18 and measured bearing 22, it is to avoid the inner ring of measured bearing 22 is contacted with pretension force loading device 18, bearing
End cap 23 is fixed with bearing block 19 by screw, and bearing bracket 20 is bolted with bearing block 19.Bearing assembly 8 is surveyed to lead to
The rotation for crossing pre-load nut 16 can promote thrust ball bearing 17, promote pretension force loading device 18 to load pretightning force indirectly, push away
Power ball bearing 17 can rotate against pre-load nut 16 and pretension force loading device 18, and then measure under different pretightning forces
Bearing dynamic stiffness.
As shown in figure 9, power transmission shaft 13 is provided with multidiameter structure 30, multiple measured bearings can be installed in multidiameter structure 30
22。
As shown in figure 1, the test device further includes exciting device and radial displacement transducer 10, exciting device set
On power transmission shaft 13, radial displacement transducer 10 is arranged between exciting device and bearing assembly to be measured 8.Radial displacement is sensed
Device 10 is arranged on base plate 1 and near measured bearing 22 by radial displacement transducer support 9.
Exciting device includes exciting disk 11 and eccentric massblock 12, and wherein exciting disk 11 is fixed on power transmission shaft 13, exciting
Multiple through holes are evenly equipped with disk 11, eccentric massblock 12 is fixed on the through hole on exciting disk 11, as shown in Figure 8.
Operation principle of the invention is：
Pretension force loading device 18 is adjusted by pre-load nut 16 in bearing assembly to be measured 6, and pre-load nut 16 is to inward turning
When turning, thrust ball bearing 17 is inwardly moved, so as to compress pretension force loading device 18, it is provided pretightning force, thrust ball bearing
17 can rotate against pre-load nut 16 and pretension force loading device 18, be more convenient to provide different pretightning forces.By pre-
The tight forward travel distance of nut 16 can calculate the pretightning force size of the offer of pretension force loading device 18.
Axial sensor 14 can measure axial displacement of the bearing under different pretightning forces, by the pretightning force that is calculated and
The axial deflection for measuring can obtain surveyed bearing axial rigidity, and being depicted as curve can then obtain bearing axial direction dynamic characteristic
Curve.
When 22 axial deformation of measured bearing is measured, exciting disk 11 and eccentric massblock 12 are shed, bearing can be measured and existed
Axial rigidity under different situations.When the timing of pretightning force one, measurement rotating speed influences on bearing rigidity；When the timing of rotating speed one, measurement is not
Bearing rigidity is influenceed with pretightning force, obtains different bearing dynamic stiffness under different pretightning forces and different rotating speeds operating mode.
Electric machine assembly 2 provides power, and the rotating speed of power transmission shaft 13 can be adjusted by accelerator 5, and electric machine assembly 2 passes through shaft coupling
Device 4 drives accelerator 5 to rotate, and accelerator 5 drives power transmission shaft 13 to rotate by shaft coupling 6, and power transmission shaft 13 drives 11 turns of exciting disk
It is dynamic so that the eccentric massblock 12 on exciting disk 11 is rotated under different rotating speeds, the quick rotation of eccentric massblock 12 produce from
Mental and physical efforts, centrifugal action in power transmission shaft 13, by power transmission shaft 13 by centrifugal action on measured bearing 22.
Electric machine assembly 2 can make the rotating speed of power transmission shaft 13 reach 15000r/min after accelerator 5 adjusts rotating speed, by swashing
The disk 11 that shakes drives eccentric massblock 12 to rotate and can provide enough eccentric forces, simulates different loads lower bearing dynamic stiffness.
The exciting of eccentric massblock 12 applies the rotation radial load with synchronization, realizes the synchronization to measured bearing 22
Excitation.Radial displacement transducer 10 measures exciting displacement of the axis system under the effect of eccentric annular flow power, is then closed according to geometry
System is conversed under equivalent load effect, the equivalent displacement produced by bearing centre.
As shown in Figure 10, the synchronous rotary radial load for being produced by eccentric mass is Q=me ω2, in formula：M is additional injustice
Weighing apparatus quality：E is the barycenter eccentric throw of additional unbalance mass, and ω is the angular speed of power transmission shaft 13.Due to using approximate side
Method, applies synchronous out-of-balance force and is not positioned immediately on bearing symmetrical plane, therefore the data obtained need to be carried out to measured bearing 22
Necessary conversion, makes result more reasonable.
The synchronous radial load for acting on measured bearing is Qe=QL1/2(1+L1+L2+L3/ 2)=me ω2L1/2(1+L1+L2+
L3/2).In formula：QeSynchronous radial load, L suffered by bearing to be measured1It is left end support bearing and the distance of exciting disk 11, L2It is exciting disk
11 with the distance of measured bearing 22, L3It is measured bearing 22 and the distance of right-hand member spring bearing, is from being Figure 10, radial displacement
Sensor 10 is disposed near measured bearing 22, and the present apparatus is converted to bearing inner race radial direction position by measuring the radial displacement of axle
Move, so radial displacement transducer 10 need to be close to measured bearing 22.
In order to more accurately characterize the radial displacement of measured bearing 22, removal main shaft is needed to bend change in itself in the calculation
The equivalent displacement of the influence of shape, i.e. axle：
δe=δc-δs；
δs=δst/(1-r2)；
δst=me ω2L2 1(L2+L3/2)2/3EI(1+L1+L2+L3/2)
In formula：δcFor the exciting displacement that test is obtained；δsFor the dynamic deflection that main shaft causes by out-of-balance force；δstScratched for quiet
Degree；R is that (critical speed measures device intrinsic frequency by experiment, and then obtains experiment dress for the ratio between running speed and critical speed
The critical speed put), E is the elastic modelling quantity of axle, and I is the moment of inertia of the axle cross section to neutral bending axis.
The radial rigidity for then testing measured bearing 22 under the corresponding each rotating speed for measuring is：
Kd=Q/ δe=QL1/2(1+L1+L2+L3/2)δe。
By changing the quality of unbalance mass, block 12 radial load can be made identical when bearing radial dynamical characteristic is measured
Measurement different rotating speeds lower bearing radial direction dynamic stiffness, the influence of analysis rotating speed all bearing radial dynamical characteristics；Difference can also be measured
The dynamic stiffness of pretightning force lower bearing, analyzes influence of the different pretightning forces to bearing radial dynamical characteristic.
Test philosophy of the present invention is correct, and consider pretightning force and radial load factor influences on bearing dynamic stiffness, simulation
Actual condition, tests different bearing dynamic characteristic parameters under different operating modes.Can regulation and control offer data online to relevant device.
Embodiments of the present invention are the foregoing is only, is not intended to limit the scope of the present invention.It is all in the present invention
Spirit and principle within any modification, equivalent substitution and improvements, the extension made etc., be all contained in protection scope of the present invention
It is interior.
Claims (10)
1. a kind of main shaft bearing joint portion device for testing dynamic stiffness, it is characterised in that：Including base plate (1) and it is arranged at base plate (1)
On electric machine assembly (2), speed probe (4), accelerator (5), spring bearing component, bearing assembly to be measured (8), power transmission shaft
(13) and shaft position sensor (14), wherein bearing assembly to be measured (8) is sheathed on the power transmission shaft (13), the power transmission shaft
(13) two ends are connected with accelerator (5) and electric machine assembly (2) successively by spring bearing modular support and one end, described turn
Fast sensor (4) and shaft position sensor (14) are respectively used to measure the rotating speed and axial displacement of the power transmission shaft (13).
2. main shaft bearing joint portion according to claim 1 device for testing dynamic stiffness, it is characterised in that：The bearing to be measured
Component (8) includes pre-load nut (16), thrust ball bearing (17), pretension force loading device (18), bearing block (19), bearing block branch
Frame (20), measured bearing (22) and bearing (ball) cover (23), wherein bearing bracket (20) are described on the base plate (1)
Bearing block (19) and bearing bracket (20) are connected, the pretension force loading device (18) is arranged in the bearing block (19),
And can axially move, the pre-load nut (16) is connected and by thrust ball axle with the threaded one end of the bearing block (19)
(17) are held to be connected with pretension force loading device (18), the measured bearing (22) be arranged at the bearing block (19) the other end,
And bearing (ball) cover (23) axial limiting by being connected with bearing block (19).
3. main shaft bearing joint portion according to claim 2 device for testing dynamic stiffness, it is characterised in that：The pretightning force adds
Carry to put and end ring (21) is provided between (18) and measured bearing (22).
4. main shaft bearing joint portion according to claim 2 device for testing dynamic stiffness, it is characterised in that：The pretightning force adds
Carry and put (18) and include outer back-up ring (24), spring support (25), spring (26), fixes sleeve (27) and inner shield ring (28), wherein
Multiple spring supports (25) with diameter parallel are connected between outer back-up ring (24) and inner shield ring (28), each spring support (25)
One end is fixedly connected with inner shield ring (28), and the other end is slidably connected with the outer back-up ring (24), is covered on each spring support (25)
Spring (26) is provided with, the fixes sleeve (27) is sheathed on the outside of the outer back-up ring (24) and inner shield ring (28).
5. main shaft bearing joint portion according to claim 4 device for testing dynamic stiffness, it is characterised in that：Described fixed cover
Be provided with chute (29) vertically on the side wall of cylinder (27), the outer back-up ring (24) and inner shield ring (28) pass through respectively screw with it is described
Chute (29) is slidably connected.
6. main shaft bearing joint portion according to claim 2 device for testing dynamic stiffness, it is characterised in that：The power transmission shaft
(13) multidiameter structure (30) is provided with, multiple measured bearings (22) can be installed on the multidiameter structure (30).
7. main shaft bearing joint portion according to claim 2 device for testing dynamic stiffness, it is characterised in that：The revolution speed sensing
Device (4) is on base plate (1) and corresponding with the output shaft of the electric machine assembly (2) by speed probe support (3)；
The shaft position sensor (14) by shaft position sensor support (15) on base plate (1) and with the transmission
The end of axle (13) is corresponding.
8. the main shaft bearing joint portion device for testing dynamic stiffness according to claim any one of 1-7, it is characterised in that：It is described
Test device further includes exciting device and radial displacement transducer (10), and the exciting device is sheathed on the power transmission shaft
(13) on, the radial displacement transducer (10) is arranged between the exciting device and the bearing assembly (8) to be measured.
9. main shaft bearing joint portion according to claim 8 device for testing dynamic stiffness, it is characterised in that：The exciting device
Including exciting disk (11) and eccentric massblock (12), wherein exciting disk (11) is fixed on power transmission shaft (13), the exciting disk
(11) multiple through holes are evenly equipped with, the eccentric massblock (12) is fixed on the through hole on exciting disk (11).
10. main shaft bearing joint portion according to claim 8 device for testing dynamic stiffness, it is characterised in that：The radial direction position
Displacement sensor (10) is by radial displacement transducer support (9) on base plate (1).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710092626.3A CN106768749B (en) | 2017-02-21 | 2017-02-21 | A kind of main shaft bearing engaging portion device for testing dynamic stiffness |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710092626.3A CN106768749B (en) | 2017-02-21 | 2017-02-21 | A kind of main shaft bearing engaging portion device for testing dynamic stiffness |
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| CN106768749B CN106768749B (en) | 2019-01-22 |
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| CN201710092626.3A Expired - Fee Related CN106768749B (en) | 2017-02-21 | 2017-02-21 | A kind of main shaft bearing engaging portion device for testing dynamic stiffness |
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