CN106768749B - A kind of main shaft bearing engaging portion device for testing dynamic stiffness - Google Patents
A kind of main shaft bearing engaging portion device for testing dynamic stiffness Download PDFInfo
- Publication number
- CN106768749B CN106768749B CN201710092626.3A CN201710092626A CN106768749B CN 106768749 B CN106768749 B CN 106768749B CN 201710092626 A CN201710092626 A CN 201710092626A CN 106768749 B CN106768749 B CN 106768749B
- Authority
- CN
- China
- Prior art keywords
- bearing
- measured
- engaging portion
- shaft
- transmission shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
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
- 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
-
- 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
-
- 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
-
- 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
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Aviation & Aerospace Engineering (AREA)
- Acoustics & Sound (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The dynamic characteristic parameter the field of test technology that the present invention relates to bearings under different operating loadings, in particular to a kind of main shaft bearing engaging portion device for testing dynamic stiffness.Including bottom plate and the electric machine assembly being set on bottom plate, speed probe, accelerator, spring bearing component, bearing assembly to be measured, exciting device, transmission shaft, shaft position sensor and radial displacement transducer, wherein bearing assembly and exciting device to be measured are sheathed on transmission shaft, the both ends of transmission shaft are successively connect with accelerator and electric machine assembly by spring bearing modular support and one end, and speed probe, shaft position sensor and radial displacement transducer are respectively used to revolving speed, axial displacement and the radial displacement of measurement transmission shaft.Present invention measurement is convenient, clear in structure, easy to operate, can imitate actual condition and measure bearing rigidity, to research bearing combining part dynamic characteristic and determines that reasonable pretightning force plays an important role.
Description
Technical field
The dynamic characteristic parameter the field of test technology that the present invention relates to bearings under different operating loadings, in particular to it is a kind of
Main shaft bearing engaging portion device for testing dynamic stiffness.
Background technique
Angular contact ball bearing is very extensive one of the part of application in machine equipments, and rigidity property directly influences master
The stiffness characteristics of axle system, especially when 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 influenced, thus the rigidity of angular contact ball bearing is studied, especially dynamic stiffness has non-
Often important meaning.
Early in eighties of last century mid-term, the researcher of the former Soviet Union to influence the engaging portion vibration problem of machine finish into
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 engaging portion, and devises small-sized testing stand and demonstrate experience calculating by regression analysis
The correctness of formula.But due to the backwardness of computer level at that time so that the solution of bearing dynamic stiffness need to expend it is a large amount of
Time.To 20 th century laters, there is a growing awareness that shadow of the dynamic property of engaging portion to heave-load device machining accuracy
It rings, people have carried out a large amount of experiment test job, rigidity, damping, modal frequency and service life including bearing etc., have accumulated big
The experimental data of amount.To 21 century, with the rapid development of electronic computer technology, researcher starts using based on hertz
The accurate iterative algorithm of contact theory and consider that various geometrical factors accurately calculate research carry out engaging portion rigidity.
Currently, in the problem of studying bearing rigidity, Static stiffness and dynamic stiffness including studying bearing.Both reflect
The ability of structure resistance to deformation, the difference is that Static stiffness refers to bearing the energy for resisting static displacement variation when steady load
Power；And dynamic stiffness refer to bear alternation dynamic loading when, resist dynamic displacement variation ability, dynamic stiffness be measure structure antivibration
The main indicator of ability, therefore bearing dynamic stiffness test is studied to the accurate spindle bearing system kinetic characteristics that obtain with important
Meaning.
The test device of test bearing engaging portion dynamic stiffness is less, and most test objects are obtained just for single bearing
Different bearing dynamic characteristic parameters under different operating conditions are taken to be of great significance.
Summary of the invention
In view of the above-mentioned problems, the purpose of the present invention is to provide a kind of main shaft bearing engaging portion device for testing dynamic stiffness, this
Device to test precision is high and is capable of measuring different bearings axially and radially dynamic characteristic parameter.
To achieve the goals above, the invention adopts the following technical scheme:
A kind of main shaft bearing engaging portion device for testing dynamic stiffness including bottom plate and the electric machine assembly being set on bottom plate, turns
Fast sensor, accelerator, spring bearing component, bearing assembly to be measured, transmission shaft and shaft position sensor, wherein bearing to be measured
Assembly set is set on the transmission shaft, the both ends of the transmission shaft by spring bearing modular support and one end successively with acceleration
Device is connected with electric machine assembly, the speed probe and shaft position sensor be respectively used to measure the revolving speed of the transmission shaft and
Axial displacement.
The bearing assembly to be measured includes pre-load nut, thrust ball bearing, pre-tightens force loading device, bearing block, bearing block
Bracket, measured bearing and bearing (ball) cover, wherein bearing bracket is mounted on the bottom plate, the bearing block and bearing bracket
Connection, the preload force loading device are set in the bearing block and can axially move, the pre-load nut and the axis
It holds the threaded one end connection of seat and is connect by thrust ball bearing with force loading device is pre-tightened, the measured bearing is set to institute
State the other end of bearing block and the bearing (ball) cover axial limiting by connecting with bearing block.
End ring is equipped between preload force loading device and the measured bearing.
The preload force loading device includes outer retaining ring, spring support, spring, fixes sleeve and inner shield ring, China and foreign countries' gear
Circle fixes company with multiple spring supports parallel with axis, one end of each spring support and inner shield ring is connected between inner shield ring
It connects, the other end is slidably connected with the outer retaining ring, and spring is arranged on each spring support, and the fixes sleeve is sheathed on described
The outside of outer retaining ring and inner shield ring.
Along being axially arranged with sliding slot on the side wall of the fixes sleeve, the outer retaining ring and inner shield ring pass through respectively screw with
The sliding slot is slidably connected.
The transmission shaft is equipped with stepped shaft structure, mountable multiple measured bearings in the stepped shaft structure.
The speed probe is mounted on the output shaft on bottom plate and with the electric machine assembly by speed probe bracket
It is corresponding；The shaft position sensor be mounted on bottom plate by shaft position sensor bracket and with the transmission shaft
End is corresponding.
The test device further comprises exciting device and radial displacement transducer, and the exciting device is sheathed on described
On transmission shaft, the radial displacement transducer is set 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 transmission shaft, the exciting
Multiple through-holes are evenly equipped on disk, the eccentric massblock is fixed on the through hole on exciting disk.
The radial displacement transducer is mounted on bottom plate by radial displacement transducer bracket.
Advantages of the present invention is with beneficial effect:
1. the present invention can provide proper axial pretightning force using force loading device and the exciting disk with eccentric mass is pre-tightened,
With different radial loads, the influence of different pretightning forces and different radial loads to bearing dynamic stiffness can be measured；
2. stepped shaft structure of the invention can be convenient a variety of different model bearings of installation, there is certain interchangeability, saves system
Cause this；
3. the present invention greatly reduces the complexity of test, easy to operate, it is easy accurately to obtain bearing dynamic characteristic
Test signal；
4. the present invention axially or radially motivates test device, bearing dynamic characteristic parameter can be accurately obtained,
Reasonable Parameters are provided to obtain bearing dynamic characteristic；
5. the present invention calculates, drive shaft displacement is eliminated, measurement model result is made more to meet reality, test knot
Fruit is more accurate；
6. different model bearing engagement surface dynamic characteristic parameter can be obtained using the device, to establish Contact characteristics
Parameter database is further fitted data in database, for select reasonable pretightning force and bearing pairing mode provide data according to
According to.
Detailed description of the invention
Fig. 1 is the structural diagram of the present invention；
Fig. 2 is the structural schematic diagram 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 that force loading device is pre-tightened in the present invention；
Fig. 6 is the axonometric drawing that force loading device is pre-tightened in the present invention；
Fig. 7 is the explosive view that force loading device is pre-tightened in the present invention；
Fig. 8 is the structural schematic diagram of exciting disk in the present invention；
Fig. 9 is the structural schematic diagram of transmission shaft in the present invention；
Figure 10 is experimental provision schematic illustration of the invention.
In figure: 1 is bottom plate, and 2 be electric machine assembly, and 3 be speed probe bracket, and 4 be speed probe, and 5 be accelerator, 6
It is the first spring bearing component for shaft coupling, 7,8 be bearing assembly to be measured, and 9 be radial displacement transducer bracket, and 10 be radial position
Displacement sensor, 11 be exciting disk, and 12 be eccentric massblock, and 13 be transmission shaft, and 14 be shaft position sensor, and 15 be axial displacement
Sensor stand, 16 be pre-load nut, and 17 be thrust ball bearing, and 18 is pre-tighten force loading device, and 19 be bearing block, and 20 be bearing
Seat support, 21 be end ring, and 22 be measured bearing, and 23 be bearing (ball) cover, and 24 be outer retaining ring, and 25 be spring support, and 26 be bullet
Spring, 27 be fixes sleeve, and 28 be inner shield ring, and 29 be sliding slot, and 30 be stepped shaft structure.
Specific embodiment
To make the objectives, technical solutions, and advantages of the present invention clearer, right in the following with reference to the drawings and specific embodiments
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 bottom plate 1 and it is mounted on bottom
Electric machine assembly 2, speed probe 4, accelerator 5, spring bearing component, bearing assembly to be measured 8, transmission shaft in the T-slot of plate 1
13 and shaft position sensor 14, wherein bearing assembly to be measured 8 is sheathed on transmission shaft 13, the both ends of transmission shaft 13 pass through support
Bearing assembly supports and one end is successively connect with accelerator 5 and electric machine assembly 2, speed probe 4 and shaft position sensor 14
It is respectively used to the revolving speed and axial displacement of measurement transmission shaft 13.
Speed probe 4 is mounted on bottom plate 1 and opposite with the output shaft of electric machine assembly 2 by speed probe bracket 3
It answers；Shaft position sensor 14 is mounted on the end phase on bottom plate 1 and with transmission shaft 13 by shaft position sensor bracket 15
It is corresponding.
As in Figure 2-4, bearing assembly 8 to be measured includes pre-load nut 16, thrust ball bearing 17, pre-tightens force loading device
18, bearing block 19, bearing bracket 20, measured bearing 22 and bearing (ball) cover 23, wherein bearing bracket 20 is mounted on bottom plate 1
On, bearing block 19 and bearing bracket 20 connect, and preload force loading device 18 is set in bearing block 19 and can be along axial shifting
Dynamic, pre-load nut 16 connect with the threaded one end of bearing block 19 and is connected by thrust ball bearing 17 and preload force loading device 18
It connects, measured bearing 22 is set to the other end of bearing block 19 and the axial limit of the bearing (ball) cover 23 by connecting with bearing block 19
Position.It pre-tightens and is equipped with end ring 21 between force loading device 18 and measured bearing 22.
As illustrated in figs. 5-7, pre-tightening force loading device 18 includes outer retaining ring 24, spring support 25, spring 26, fixes sleeve 27
And inner shield ring 28, multiple spring supports 25 parallel with axis, each spring are connected between China and foreign countries' retaining ring 24 and inner shield ring 28
One end of bracket 25 is fixedly connected with inner shield ring 28, and the other end is slidably connected with outer retaining ring 24, is arranged on each spring support 25
There is spring 26, fixes sleeve 27 is sheathed on the outside of outer retaining ring 24 and inner shield ring 28.
Along sliding slot 29 is axially arranged on the side wall of fixes sleeve 27, outer retaining ring 24 and inner shield ring 28 pass through screw and cunning respectively
Slot 29 is slidably connected.Spring 26, which is under different compressive states, can provide different pretightning forces, and fixes sleeve 27 can prevent outer
Retaining ring 24 and inner shield ring 28 relatively rotate.
Further, pre-load nut 16 has boss to prop up jointly with the end for pre-tightening the outer retaining ring 24 in force loading device 18
Thrust ball bearing 17 is supportted, pre-tightens force loading device 18 by threaded portion sub-support non-in bearing block 19, end ring 21 is placed on pre-
Between clamp force loading device 18 and measured bearing 22,22 inner ring of measured bearing is avoided to contact with force loading device 18 is pre-tightened, bearing
End cap 23 is fixed with bearing block 19 by screw, and bearing bracket 20 is bolted with bearing block 19.It is logical to survey bearing assembly 8
The rotation for crossing pre-load nut 16 can push thrust ball bearing 17, push indirectly and pre-tighten the load pretightning force of force loading device 18, push away
Power ball bearing 17 can make pre-load nut 16 and pre-tighten the generation relative rotation of force loading device 18, and then measure under different pretightning forces
Bearing dynamic stiffness.
As shown in figure 9, transmission shaft 13 is equipped with stepped shaft structure 30, mountable multiple measured bearings in stepped shaft structure 30
22。
As shown in Figure 1, the test device further comprises exciting device and radial displacement transducer 10, exciting device set
On transmission shaft 13, radial displacement transducer 10 is set between exciting device and bearing assembly to be measured 8.Radial displacement sensing
Device 10 is mounted on bottom plate 1 by radial displacement transducer bracket 9 and close to measured bearing 22.
Exciting device includes exciting disk 11 and eccentric massblock 12, and wherein exciting disk 11 is fixed on transmission shaft 13, exciting
Multiple through-holes are evenly equipped on disk 11, eccentric massblock 12 is fixed on the through hole on exciting disk 11, as shown in Figure 8.
The working principle of the invention is:
It pre-tightens force loading device 18 to be adjusted by pre-load nut 16 in bearing assembly 6 to be measured, pre-load nut 16 is to inward turning
When turning, thrust ball bearing 17 is inwardly moved, and pre-tightens force loading device 18 to compress, it is made to provide pretightning force, thrust ball bearing
17 can make pre-load nut 16 and pre-tighten the generation relative rotation of force loading device 18, be more convenient to provide different pretightning forces.By pre-
Tight 16 forward travel distance of nut, which can calculate, pre-tightens the pretightning force size that force loading device 18 provides.
Axial sensor 14 can measure axial displacement of the bearing under different pretightning forces, by the pretightning force that is calculated and
Available the surveyed bearing axial rigidity of the axial deflection measured is depicted as curve then available bearing axial direction dynamic characteristic
Curve.
When measuring 22 axial deformation of measured bearing, exciting disk 11 and eccentric massblock 12 are shed, bearing can be measured and existed
Axial rigidity under different situations.When one timing of pretightning force, measurement revolving speed influences bearing rigidity；When one timing of revolving speed, measurement is not
Bearing rigidity is influenced with pretightning force, obtains different bearing dynamic stiffness under different pretightning forces and different rotating speeds operating condition.
Electric machine assembly 2 provides power, and by the revolving speed of the adjustable transmission shaft 13 of accelerator 5, electric machine assembly 2 passes through shaft coupling
Device 4 drives accelerator 5 to rotate, and accelerator 5 drives transmission shaft 13 to rotate by shaft coupling 6, and transmission shaft 13 drives 11 turns of exciting disk
It is dynamic, so that the eccentric massblock 12 on exciting disk 11 be made to rotate under different rotating speeds, 12 quick rotation of eccentric massblock generate from
Mental and physical efforts, centrifugal force act on transmission shaft 13, are acted on centrifugal force on measured bearing 22 by transmission shaft 13.
Electric machine assembly 2 can make 13 revolving speed of transmission shaft reach 15000r/min after adjusting revolving speed by accelerator 5, by swashing
Vibration plate 11 drives the rotation of eccentric massblock 12 that can provide enough eccentric forces, simulates different loads lower bearing dynamic stiffness.
12 exciting of eccentric massblock applies the rotation radial load synchronous with revolving speed, 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 converses under equivalent load effect, equivalent displacement caused by bearing centre.
It as shown in Figure 10, is Q=me ω by the synchronous rotary radial force that eccentric mass generates2, in formula: m is additional injustice
Weighing apparatus quality: e is the mass center eccentricity of additional unbalance mass, and ω is the angular speed of transmission shaft 13.Due to using approximation side
Method applies synchronous out-of-balance force to measured bearing 22 and is not positioned immediately on bearing symmetrical plane, therefore needs to carry out to the data obtained
Necessary conversion keeps result more reasonable.
The synchronization radial force 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 force, L suffered by bearing to be measured1For left end support bearing and 11 distance of exciting disk, L2For exciting disk
11 with 22 distance of measured bearing, L3Be measured bearing 22 at a distance from right end spring bearing, for by for Figure 10 it is found that radial displacement
Sensor 10 is disposed close to measured bearing 22, and the present apparatus is converted to bearing inner race radial direction position by measuring the radial displacement of axis
It moves, so radial displacement transducer 10 is needed close to measured bearing 22.
In order to more accurately characterize the radial displacement of measured bearing 22, needs to remove main shaft itself in calculating and be bent change
The influence of shape, the i.e. equivalent displacement of axis:
δe=δc-δs；
δs=δst/(1-r2)；
δst=me ω2L2 1(L2+L3/2)2/3EI(1+L1+L2+L3/2)
In formula: δcTo test the displacement of obtained exciting；δsIt is main shaft because of dynamic deflection caused by out-of-balance force；δstIt is scratched to be 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 set), E is the elasticity modulus of axis, and I is the moment of inertia of the shaft cross section to neutral bending axis.
Then test the radial rigidity of measured bearing 22 under the corresponding each revolving speed measured are as follows:
Kd=Q/ δe=QL1/2(1+L1+L2+L3/2)δe。
Radial force can be kept identical by changing the quality of unbalance mass, block 12 when measuring bearing radial dynamical characteristic
Measure different rotating speeds lower bearing radial direction dynamic stiffness, the influence of analysis revolving 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 comprehensively considering pretightning force and radial load factor influences bearing dynamic stiffness, simulation
Actual condition tests different bearing dynamic characteristic parameters under different operating conditions.Relevant device can be regulated and controled provide data online.
Mode the above is only the implementation of the present invention 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 replacement, improvement, extension etc., be all contained in protection scope of the present invention
It is interior.
Claims (9)
1. a kind of main shaft bearing engaging portion device for testing dynamic stiffness, it is characterised in that: including bottom plate (1) and be set to bottom plate (1)
On electric machine assembly (2), speed probe (4), accelerator (5), spring bearing component, bearing assembly to be measured (8), transmission shaft
(13) and shaft position sensor (14), wherein bearing assembly to be measured (8) is sheathed on the transmission shaft (13), the transmission shaft
(13) both ends are successively connect with accelerator (5) and electric machine assembly (2) by spring bearing modular support and one end, and described turn
Fast sensor (4) and shaft position sensor (14) are respectively used to measure the revolving speed and axial displacement of the transmission shaft (13)；
The bearing assembly to be measured (8) includes pre-load nut (16), thrust ball bearing (17), pre-tightens force loading device (18), axis
Seat (19), bearing bracket (20), measured bearing (22) and bearing (ball) cover (23) are held, wherein bearing bracket (20) is mounted on institute
It states on bottom plate (1), the bearing block (19) and bearing bracket (20) connection, the preload force loading device (18) are set to institute
It states in bearing block (19) and can axially move, the pre-load nut (16) connect with the threaded one end of the bearing block (19),
And connect by thrust ball bearing (17) with force loading device (18) are pre-tightened, the measured bearing (22) is set to the bearing block
(19) the other end and bearing (ball) cover (23) axial limiting by being connect with bearing block (19).
2. main shaft bearing engaging portion according to claim 1 device for testing dynamic stiffness, it is characterised in that: the pretightning force adds
It carries to set and is equipped with end ring (21) between (18) and measured bearing (22).
3. main shaft bearing engaging portion according to claim 1 device for testing dynamic stiffness, it is characterised in that: the pretightning force adds
Carrying and setting (18) includes outer retaining ring (24), spring support (25), spring (26), fixes sleeve (27) and inner shield ring (28), wherein
Multiple spring supports parallel with axis (25) are connected between outer retaining 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 retaining ring (24), is covered on each spring support (25)
Equipped with spring (26), the fixes sleeve (27) is sheathed on the outside of the outer retaining ring (24) and inner shield ring (28).
4. main shaft bearing engaging portion according to claim 3 device for testing dynamic stiffness, it is characterised in that: the fixing sleeve
Along being axially arranged with sliding slot (29) on the side wall of cylinder (27), the outer retaining ring (24) and inner shield ring (28) pass through respectively screw with it is described
Sliding slot (29) is slidably connected.
5. main shaft bearing engaging portion according to claim 1 device for testing dynamic stiffness, it is characterised in that: the transmission shaft
(13) stepped shaft structure (30) are equipped with, mountable multiple measured bearings (22) on the stepped shaft structure (30).
6. main shaft bearing engaging portion according to claim 1 device for testing dynamic stiffness, it is characterised in that: the revolution speed sensing
Device (4) is mounted on bottom plate (1) and corresponding with the output shaft of the electric machine assembly (2) by speed probe bracket (3)；
The shaft position sensor (14) by shaft position sensor bracket (15) be mounted on bottom plate (1) and with the transmission
The end of axis (13) is corresponding.
7. main shaft bearing engaging portion according to claim 1-6 device for testing dynamic stiffness, it is characterised in that: described
Test device further comprises exciting device and radial displacement transducer (10), and the exciting device is sheathed on the transmission shaft
(13) on, the radial displacement transducer (10) is set between the exciting device and the bearing assembly to be measured (8).
8. main shaft bearing engaging portion according to claim 7 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 transmission shaft (13), the exciting disk
(11) multiple through-holes are evenly equipped on, the eccentric massblock (12) is fixed on the through hole on exciting disk (11).
9. main shaft bearing engaging portion according to claim 7 device for testing dynamic stiffness, it is characterised in that: the radial displacement
Sensor (10) is mounted on bottom plate (1) by radial displacement transducer bracket (9).
Priority Applications (1)
| 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 |
Applications Claiming Priority (1)
| 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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106768749A CN106768749A (en) | 2017-05-31 |
| CN106768749B true CN106768749B (en) | 2019-01-22 |
Family
ID=58958347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| 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 |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106768749B (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107727390B (en) * | 2017-08-21 | 2019-07-16 | 江铃汽车股份有限公司 | Automobile power-transmission system flexural property test method |
| CN109799088A (en) * | 2017-11-14 | 2019-05-24 | 东北林业大学 | A kind of radial direction hydrostatic gas-lubricated bearing experiment test device |
| CN109855867B (en) * | 2017-11-30 | 2021-01-22 | 洛阳轴承研究所有限公司 | Loading device integrating axial load loading and rotary load loading |
| CN109855868B (en) * | 2017-11-30 | 2021-01-22 | 洛阳轴承研究所有限公司 | Dynamic test method and test equipment for axial stiffness of bearing |
| CN107843432B (en) * | 2017-11-30 | 2024-02-09 | 北京航天动力研究所 | Dynamic stiffness measuring device for bearing |
| CN107894336A (en) * | 2017-12-11 | 2018-04-10 | 重庆长江轴承股份有限公司 | Deep groove ball bearing radial loaded formula rigidity detection device |
| CN107917807B (en) * | 2017-12-29 | 2019-10-11 | 中国科学院沈阳自动化研究所 | A kind of device based on rotor-bearing system test Dynamic Characteristics of Rolling Element Bearings |
| CN108132187A (en) * | 2018-01-30 | 2018-06-08 | 中国航空发动机研究院 | Rolling bearing static rigidity detection device |
| CN108414171A (en) * | 2018-03-15 | 2018-08-17 | 中国航空发动机研究院 | Rolling bearing dynamic rate detection device |
| CN110220705A (en) * | 2019-06-14 | 2019-09-10 | 人本集团有限公司 | Bearing centrifugal test platform |
| CN110567718B (en) * | 2019-08-29 | 2020-12-18 | 西安理工大学 | Rolling bearing radial dynamic stiffness testing device based on piezoelectric actuator |
| CN111323230A (en) * | 2020-03-27 | 2020-06-23 | 人本集团有限公司 | Test equipment for truck or automobile clutch bearing |
| CN113607416B (en) * | 2021-08-04 | 2023-05-30 | 大连工业大学 | Rolling bearing three-dimensional dynamic stiffness test device and test method thereof |
| CN114878163B (en) * | 2022-05-18 | 2024-01-23 | 哈尔滨工业大学 | Dynamic and static synchronous loading testing device for high-precision dynamic pressure thrust foil bearing |
| CN117433783B (en) * | 2023-08-29 | 2024-05-24 | 大连海事大学 | Tapered roller bearing positioning pre-tightening adjustment method and device based on axial rigidity detection |
| CN117664419B (en) * | 2024-02-02 | 2024-04-05 | 哈尔滨工业大学 | Hole shaft interference fit contact surface radial force and binding force testing system and measuring method |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101936810A (en) * | 2010-08-02 | 2011-01-05 | 沈机集团昆明机床股份有限公司 | Comprehensive test experiment device for dynamic and static properties of rolling bearing-main shaft system |
| KR20110109525A (en) * | 2010-03-31 | 2011-10-06 | 창원대학교 산학협력단 | Measuring apparatus for dynamic stiffness |
| CN102279104A (en) * | 2011-03-15 | 2011-12-14 | 吉林大学 | Bearing combination part characteristic test bed |
| CN102331349A (en) * | 2011-06-17 | 2012-01-25 | 武汉理工大学 | Permanent magnetic bearing rigidity measuring device |
| CN102426085A (en) * | 2011-08-19 | 2012-04-25 | 西安理工大学 | Device and method for testing contact rigidity of spherical surface-rotary surface combining surface |
| CN102607847A (en) * | 2012-03-08 | 2012-07-25 | 北京工业大学 | Dynamic stiffness test device of main shaft bearing combination part |
| CN103105296A (en) * | 2013-01-23 | 2013-05-15 | 南京理工大学 | Testing device for bearing dynamic characteristic parameters |
| CN205067088U (en) * | 2015-08-25 | 2016-03-02 | 北京航天动力研究所 | Radial quiet firm measuring device of angular contact ball bearing |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007088698A1 (en) * | 2006-01-31 | 2007-08-09 | Ntn Corporation | Bearing device for drive wheel |
-
2017
- 2017-02-21 CN CN201710092626.3A patent/CN106768749B/en not_active Expired - Fee Related
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20110109525A (en) * | 2010-03-31 | 2011-10-06 | 창원대학교 산학협력단 | Measuring apparatus for dynamic stiffness |
| CN101936810A (en) * | 2010-08-02 | 2011-01-05 | 沈机集团昆明机床股份有限公司 | Comprehensive test experiment device for dynamic and static properties of rolling bearing-main shaft system |
| CN102279104A (en) * | 2011-03-15 | 2011-12-14 | 吉林大学 | Bearing combination part characteristic test bed |
| CN102331349A (en) * | 2011-06-17 | 2012-01-25 | 武汉理工大学 | Permanent magnetic bearing rigidity measuring device |
| CN102426085A (en) * | 2011-08-19 | 2012-04-25 | 西安理工大学 | Device and method for testing contact rigidity of spherical surface-rotary surface combining surface |
| CN102607847A (en) * | 2012-03-08 | 2012-07-25 | 北京工业大学 | Dynamic stiffness test device of main shaft bearing combination part |
| CN103105296A (en) * | 2013-01-23 | 2013-05-15 | 南京理工大学 | Testing device for bearing dynamic characteristic parameters |
| CN205067088U (en) * | 2015-08-25 | 2016-03-02 | 北京航天动力研究所 | Radial quiet firm measuring device of angular contact ball bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106768749A (en) | 2017-05-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106768749B (en) | A kind of main shaft bearing engaging portion device for testing dynamic stiffness | |
| CN101246071B (en) | Shafting dynamic balance experimental bench | |
| CN102269654A (en) | Water lubricated bearing and transmission system comprehensive performance testing platform | |
| CN202735085U (en) | Main shaft performance testing platform | |
| CN102607847A (en) | Dynamic stiffness test device of main shaft bearing combination part | |
| CN112179690B (en) | Test bed for testing sealing performance of heavy pressure centrifuge | |
| CN102519639A (en) | Friction torque measurement apparatus of horizontal bearing | |
| CN103344553A (en) | High-speed rolling contact fatigue testing machine | |
| CN109876931A (en) | A kind of hypergravity centrifuge amount of unbalance monitoring method | |
| CN110542556A (en) | Tilting pad sliding bearing test box, test bench and test method | |
| CN106017758A (en) | Online synchronous test device and method for dynamic/static torque of motor | |
| CN110006659A (en) | A kind of gear drive Duct-Burning Turbofan low pressure rotor system model exerciser | |
| CN210487269U (en) | Tilting pad sliding bearing test box and test bench | |
| CN203337382U (en) | Bearing precision performance testing device | |
| CN113607416A (en) | Rolling bearing three-dimensional dynamic stiffness test device and test method thereof | |
| CN109115408A (en) | A kind of Large Hydropower Station dynamic balance running method based on centrifugal force equation | |
| Hou et al. | Vibration analysis of ball bearing considering waviness under high speed and an axial load | |
| Wu et al. | Theoretical calculation models and measurement of friction torque for rolling bearings: state of the art | |
| CN103674504A (en) | Main shaft performance testing platform | |
| CN107917807B (en) | A kind of device based on rotor-bearing system test Dynamic Characteristics of Rolling Element Bearings | |
| CN217687779U (en) | Rolling bearing rigidity testing device | |
| CN115950581A (en) | Calibration device and method for rotor shaft squirrel cage force measurement structure | |
| Yun et al. | A new dynamic balancing method of spindle based on the identification energy transfer coefficient | |
| CN203894018U (en) | Three-span rotor vibration test platform | |
| RU49256U1 (en) | TESTING BEARING TEST PLANT |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20190122 Termination date: 20210221 |