CN202033190U - Bearing combining part characteristic experiment table - Google Patents
Bearing combining part characteristic experiment table Download PDFInfo
- Publication number
- CN202033190U CN202033190U CN2011200677606U CN201120067760U CN202033190U CN 202033190 U CN202033190 U CN 202033190U CN 2011200677606 U CN2011200677606 U CN 2011200677606U CN 201120067760 U CN201120067760 U CN 201120067760U CN 202033190 U CN202033190 U CN 202033190U
- Authority
- CN
- China
- Prior art keywords
- bearing
- guide pin
- screw rod
- pin bushing
- joint portion
- 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
Images
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
The present utility model relates to a bearing combining part characteristic experiment table which belongs to the mechanical manufacture field. A bearing assembly, an axial loading mechanism and a radial loading mechanism can be connected on a platform through bolts, wherein the radial loading mechanism can slide in a platform T-shaped groove through a positioning button connected on a portal bottom surface. The bearing assembly is composed of a bearing pedestal, a bearing, a shaft, an isolating sleeve, a bearing cover, and the like. The research on the bearing combining part characteristic done by the experiment table can provide parameter supports for the CAE simulation analysis of the precision machine tool development, and the efficiency of developing machine tools can be increased. Moreover, the research method of the bearing combining part used by the experiment table can be expanded to other non machine tool fields which comprise bearing assemblies.
Description
Technical field
The utility model relates to the experimental provision of a kind of bearing joint portion characteristic research, specifically is at the experiment table of main shaft of numerical control machine tool bearing joint portion characteristic research, belongs to mechanical manufacturing field.
Background technology
Progressively adopted the design concept of CAD/CAE/CAM in the China NC Machine exploitation, tried hard to accurately reflect the performances such as machining precision of machine tool product in the design phase.Present domestic lathe manufacturing enterprise begins to adopt the CAE technology that the machine tool product of designed exploitation is carried out dynamic and static, hot performance analysis, but in most cases lathe analysis result and lathe actual performance differ bigger, analysis result still can not be as believable design considerations, can only adopt the performance history of " design one development one test one is revised ", cause the product development cycle long, cost is high.Its main cause is the machine tool structure complexity, exist various faying faces, faying face is very obvious to the influence of machine dynamic characteristics, and the influence factor of faying face characteristic and influence rule very the complexity, determining the confidence level of analysis result to a great extent, the faying face characteristic research becomes one of bottleneck problem of condition number controlled machine design.
Improve the designing quality of machine tool product, improve dynamic and static, the hot performance of machine tool product, shorten the cycle that machine tool product is developed, press for research and set up method for analyzing performance and the platform that a cover is supported the machine tool product design.In theoretical analysis and experimental study that the machine tool capability designing institute relates to, the problem of labyrinth faying face Contact Dynamics modeling will be related to inevitably.Faying face contact performance modeling of parameters method and forecasting techniques for lathe are studied, and help to set up the theoretical analysis model of more realistic machine tool structure.Thereby make in the drawing design phase, just can be by certain analytical calculation, the prediction lathe property so that can in time find the weak link of structure, carries out structural modification.This is for the designing quality that improves machine tool product, and the shortening machine tool product structure typing cycle has great importance.
Except main motions such as planer, broaching machine are straight-line lathe, most of lathes all have spindle unit, spindle unit is the particularly critical function parts of precision machine tool of lathe, and its kinematic accuracy and the rigidity of structure are the key factors of decision machine tooling quality and stock-removing efficiency.Bearing assembly in the axis system has material impact to running accuracy, rigidity and the velocity adaptive of axis system, the bearing joint portion is the core of spindle assemblies, its The Characteristic Study is significant for the reliability that improves the principal axis system simulation analysis in the design phase, also is to improve the development efficiency of lathe and an important step of designing quality.
The bearing joint portion comprises faying face three parts of faying face, bearing inner race and the axle of bearing, bearing outer ring and bearing saddle bore.Bearing is widely used in the machine tool assembly, and bearing joint portion characteristic has significant effects to the kinematic behavior of physical construction, and along with improving constantly of machine finish, this influence is more remarkable.Because the non-linear characteristics and the bearing assembly assembly relation complexity of bearing rigidity are difficult to obtain reliable sound attitude parameter by Theoretical Calculation; The data of obtaining by experiment are limited.
Summary of the invention
The experiment table of a kind of bearing joint portion characteristic research that the utility model provides, can study the quiet dynamic characteristic of bearing joint portion, can provide hardware supported and parameter support for the joint portion parameter database that improves machine tool development efficient and the required foundation of designing quality.
The technical scheme that the utility model is taked is: bearing assembly, axial load maintainer, radial loaded mechanism are connected on the platform that has T type groove by bolt.
The utility model bearing assembly structure is: bearing is arranged in bearing seat, and axle is rotationally connected with bearing, and bearing inner race spacer, bearing outer ring spacer are socketed in the outside of axle respectively, and bearing cap is fixedlyed connected with bearing seat, and the adjustment pad is arranged between bearing cap and bearing seat.
The structure of the axial load maintainer of the utility model is, handle one and nut one are by being threaded, nut one is connected by straight pin one with the axial screw rod that loads, axially briquetting is fixedlyed connected with the axial screw rod end that loads, the axial screw rod that loads is rotationally connected with axial guide pin bushing, and axially guide pin bushing is connected with axial guide pin bushing support fixation.
The structure of the utility model radial loaded mechanism is: handle two and nut two pass through thread connection, nut two and radial loaded screw rod connect by straight pin two, radially briquetting is fixedlyed connected with radial loaded screw rod lower end, the radial loaded screw rod is rotationally connected with guide pin bushing radially, radially guide pin bushing is fixedlyed connected with gantry, and radially the guide pin bushing support set is outside and fixedly connected with gantry at guide pin bushing radially.
Advantage of the present utility model is:
(1) utilizes axial load maintainer, radial loaded mechanism and test macro can realize quiet, the dynamic characteristic of bearing joint portion are studied simultaneously, the research of quiet dynamic characteristic is incorporated on the experiment table.
(2) experiment table is studied four kinds of influence factors, can the situation that influence factor and influence factor comprise be increased as required, and platform, load maintainer and test macro need not change, and increasing and change bearing assembly can realize.
(3) design of experiment table taken into full account the existence form of lathe main shaft bearing combination of components face commonly used and load action mode, adopted suitable bearing assembly assembling and load maintainer to make on the testing table joint portion and actual machine tool mainshaft bearing assembly centre bearer joint portion working condition consistent.
(4) utilize this bearing joint portion experiment table can obtain the quiet dynamic characteristic parameter of a large amount of bearing faying faces, to set up faying face characterisitic parameter database.To the further match of the data in the database, can obtain the characterisitic parameter of the bearing of arbitrary dimension, model and kind in the scope.
Description of drawings
Fig. 1 is a structural representation of the present utility model.
Fig. 2 is the structural representation of the fashionable bearing assembly of the face-to-face bearing pack of biserial of the present utility model.
Fig. 3 is the structural representation of the axial load maintainer of the utility model.
Fig. 4 is the structural representation of the utility model radial loaded mechanism.
Fig. 5 is that the utility model embodiment 1 is the structural representation of bearing assembly when axially loading.
Fig. 6 is the structural representation of the utility model embodiment 2 when being radial loaded.
Embodiment
The utility model bearing assembly structure is: bearing 105 is arranged in bearing seat 104, axle 102 is rotationally connected with bearing 105, bearing inner race spacer 106, bearing outer ring spacer 107 are socketed in the outside of axle respectively, bearing cap 101 is fixedlyed connected with bearing seat, and the pad 103 of adjustment is arranged between bearing cap 101 and bearing seat.
The structure of the axial load maintainer of the utility model is, handle 1 and nut 1 are by being threaded, nut one is connected by straight pin 1 with the axial screw rod 402 that loads, axially briquetting 407 is fixedlyed connected with the axial screw rod end that loads, the axial screw rod that loads is rotationally connected with axial guide pin bushing 405, and axial guide pin bushing supports 406 with axial guide pin bushing fixedlys connected.
The structure of the utility model radial loaded mechanism is: handle 2 201 and nut 2 203 pass through thread connection, nut two and radial loaded screw rod 207 connect by straight pin 2 202, radially briquetting 208 is fixedlyed connected with radial loaded screw rod 207 lower ends, the radial loaded screw rod is rotationally connected with guide pin bushing 205 radially, radially guide pin bushing is fixedlyed connected with gantry 204, and radially guide pin bushing supports 206 to be enclosed within radially guide pin bushing outside and fixedly connected with gantry.
Below in conjunction with accompanying drawing two kinds of embodiment of the present utility model are described in further detail.
Embodiment 1:
The general structure of present embodiment as shown in Figure 5, wherein axially the structure of load maintainer 4 as shown in Figure 3, the structure of bearing assembly 1 as shown in Figure 2, axially load maintainer 4 and bearing assembly 1 are cemented on the platform 3 by bolt.Handle 1 and nut 1 pass through thread connection, nut 1 and the axial screw rod 402 that loads connect by straight pin 1, the twisting resistance that acts on handle 1 is passed to axial loading screw rod 402 by nut 1, axially loading screw rod 402 rotates and moves axially along the screw thread raceway, axially load moving axially of screw rod 402 and make the end face of the axial briquetting 407 of its end connection by force transducer 5 axial compression bearing assembly axis 102, bearing assembly 1 is applied axial load, and load value can record by the force transducer 5 that is connected between briquetting 407 and axle 102 end faces; Under the effect of loading force, the bearing 105 of bearing assembly 1 produces axial deformation, deflection can be reflected by the displacement of axle 102 other ends, can record the displacement of axle 102 end faces by measuring systems such as laser interferometer, and then draw the axial deformation of bearing joint portion, can get the axial rigidity of bearing joint portion by loading force and axial deflection.
Embodiment 2:
The general structure of present embodiment as shown in Figure 6, wherein the structure of radial loaded mechanism 2 as shown in Figure 4, the structure of bearing assembly 1 as shown in Figure 2, two radial loaded mechanisms 2 and bearing assembly 1 are cemented on the platform 3 by bolt.Gantry 204 and radially guide pin bushing support 206, radially guide pin bushing support 206 with guide pin bushing 205 radially all be to pass through Bolt Connection, handle 2 201 and nut 2 203 pass through thread connection, nut 2 203 and radial loaded screw rod 207 connect by straight pin 2 202, the twisting resistance that acts on handle 2 201 is passed to radial loaded screw rod 207 by nut 2 203, radial loaded screw rod 207 rotates and moves axially along the screw thread raceway, the moving axially of radial loaded screw rod 207 makes radially briquetting 208 that its end the connects upper edge by the end shaft part of force transducer 6 axial compression bearing assembly axis 102, two radial loaded mechanisms apply radial load to bearing assembly 1 simultaneously at the two ends of axle 102, and load value can record by the force transducer 6 that is connected between briquetting 208 radially and axle 102 end faces; Under the effect of loading force, the bearing 105 of bearing assembly 1 produces radial deformation, the distortion of axle itself is much smaller than the distortion of bearing joint portion in theory, so the deflection of bearing joint portion can be reflected by the displacement of the following tangent plane of axle 102 end shaft parts, can record the displacement of axle 102 end shaft part incision faces by measuring systems such as laser interferometer, and then draw the radial deformation of bearing joint portion, can get the radial rigidity of bearing joint portion by loading force and radial-deformation.
Experiment table has taken into full account the situation of the main shaft of numerical control machine tool bearing faying face of practical study, therefrom selected bearing joint portion four kinds of bigger factors of influence are studied, realize the change of correlative factor by changing bearing assembly, other factor of not considering all adopts a kind of the most frequently used situation in the numerically-controlled machine series of being studied; Bearing assembly and load maintainer all can be by Bolt Connection on the platforms that has T type groove, and radial loaded mechanism can also slide in platform T type groove by the positioning key that bottom surface, gantry connects; Axially load maintainer and radial loaded mechanism load bearing assembly, measure respectively axially and the loading force radially and the displacement of bearing joint portion by force transducer and displacement transducer, and then obtain the quiet rigidity of bearing joint portion; For the kinetic model of bearing joint portion, be that the bearing joint portion is considered as integral body, do not consider bearing quality, promptly between axle and bearing saddle bore, directly be connected with damping with some rigidity; Utilize dynamic test equipment that bearing assembly is carried out the modal parameter that exciting, pick-up, data acquisition and processing (DAP) obtain bearing assembly later on, utilize certain approximating method to obtain the dynamic rate and the damping of bearing joint portion at last; Obtain after quiet rigidity, dynamic stiffness and the damping of different factor lower bearings joint portion, can analyze the influence rule of different influence factors bearing joint portion characteristic.
Four kinds of influence factors comprise bearing bore diameter, bearing array mode, bearing contact angle and pretightning force, and experiment table is studied the influence of the quiet dynamic characteristic in bearing joint portion four kinds of factors by changing bearing assembly; 70 serial angular contact ball bearings with different inner diameters and different contact angles during the experiment of this experiment table experimentize, 50,70,90,100,120,150 6 kind bearing bore diameter is got:, contact angle is got 15 °, 25 °, 30 ° three kinds, that pretightning force is divided is light, in, weigh three kinds, that the bearing array mode has is single-row, biserial face-to-face, biserial back-to-back, three row face-to-face, three row, five kinds of situations back-to-back; Different inner diameters bearing and different axle and bearing seat cooperations are formed different bearing assemblies, shared identical axial load maintainer of different bearing assemblies and radial loaded mechanism with some other auxiliary member.
Claims (4)
1. bearing joint portion characteristic test platform is characterized in that: bearing assembly, axially load maintainer, radial loaded mechanism are connected on the platform that has T type groove by bolt.
2. bearing according to claim 1 joint portion characteristic test platform, it is characterized in that: the bearing assembly structure is: bearing is arranged in bearing seat, axle is rotationally connected with bearing, bearing inner race spacer, bearing outer ring spacer are socketed in the outside of axle respectively, bearing cap is fixedlyed connected with bearing seat, and the adjustment pad is arranged between bearing cap and bearing seat.
3. bearing according to claim 1 joint portion characteristic test platform, it is characterized in that: axially the structure of load maintainer is, handle one and nut one are by being threaded, nut one is connected by straight pin one with the axial screw rod that loads, axially briquetting is fixedlyed connected with the axial screw rod end that loads, the axial screw rod that loads is rotationally connected with axial guide pin bushing, and axially guide pin bushing is connected with axial guide pin bushing support fixation.
4. bearing according to claim 1 joint portion characteristic test platform, it is characterized in that: the structure of radial loaded mechanism is: handle two and nut two pass through thread connection, nut two and radial loaded screw rod connect by straight pin two, radially briquetting is fixedlyed connected with radial loaded screw rod lower end, the radial loaded screw rod is rotationally connected with guide pin bushing radially, radially guide pin bushing is fixedlyed connected with gantry, and radially the guide pin bushing support set is outside and fixedly connected with gantry at guide pin bushing radially.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200677606U CN202033190U (en) | 2011-03-15 | 2011-03-15 | Bearing combining part characteristic experiment table |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200677606U CN202033190U (en) | 2011-03-15 | 2011-03-15 | Bearing combining part characteristic experiment table |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202033190U true CN202033190U (en) | 2011-11-09 |
Family
ID=44895484
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200677606U Expired - Fee Related CN202033190U (en) | 2011-03-15 | 2011-03-15 | Bearing combining part characteristic experiment table |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202033190U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102279104A (en) * | 2011-03-15 | 2011-12-14 | 吉林大学 | Bearing combination part characteristic test bed |
| CN102678074A (en) * | 2012-06-11 | 2012-09-19 | 江苏省无锡探矿机械总厂有限公司 | Box opening type rotator |
| CN105258888A (en) * | 2015-11-13 | 2016-01-20 | 西安交通大学 | Research experiment apparatus and measurement method for influences of bearing interference on main shaft system performance |
-
2011
- 2011-03-15 CN CN2011200677606U patent/CN202033190U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102279104A (en) * | 2011-03-15 | 2011-12-14 | 吉林大学 | Bearing combination part characteristic test bed |
| CN102678074A (en) * | 2012-06-11 | 2012-09-19 | 江苏省无锡探矿机械总厂有限公司 | Box opening type rotator |
| CN105258888A (en) * | 2015-11-13 | 2016-01-20 | 西安交通大学 | Research experiment apparatus and measurement method for influences of bearing interference on main shaft system performance |
| CN105258888B (en) * | 2015-11-13 | 2018-01-19 | 西安交通大学 | Research experiment device and measuring method of the bearing magnitude of interference to axis system performance impact |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102279104A (en) | Bearing combination part characteristic test bed | |
| CN106202647B (en) | Multi-axis fatigue life prediction method and fatigue life reliability evaluation method for electric spindle | |
| Mi et al. | Effects of preloads on joints on dynamic stiffness of a whole machine tool structure | |
| Altintas et al. | Virtual design and optimization of machine tool spindles | |
| Jorgensen et al. | Dynamics of spindle-bearing systems at high speeds including cutting load effects | |
| CN107688716B (en) | Hollow cylindrical roller bearing parameter optimization method based on load distribution and fatigue life | |
| CN202033190U (en) | Bearing combining part characteristic experiment table | |
| Cao | Modeling of high-speed machine-tool spindle systems | |
| Yang et al. | Static and dynamic characteristics modeling for CK61125 CNC lathe bed basing on FEM | |
| Miao et al. | Dynamic analysis of the column-spindle system considering the nonlinear characteristics of kinematic joints | |
| CN103286635A (en) | Numerically controlled lathe prototype testing process and evaluation method | |
| CN1979120A (en) | Method for predicting performace of simulated numerical-control machine tool | |
| Delgado et al. | Analysis of non-linear machine tool dynamic behavior | |
| Wrzochal et al. | New device proposed for industrial measurement of rolling bearing friction torque | |
| Jin et al. | Reliability coupling mechanism analyses of T-rotation-type CMA with frame deformation in CNC machine tools | |
| Feng et al. | Analysis of static and dynamic characteristic of spindle system and its structure optimization in camshaft grinding machine | |
| CN101690980A (en) | Machine tool design method | |
| CN103925898A (en) | Method for directly measuring protruding amount of face-to-face angular contact bearing | |
| Andoko et al. | Simulation of CNC milling 5 axis with finite element method | |
| Fuzhong | CNC milling machine spindle characteristics analysis by FEM | |
| Chen et al. | Contact stress and radial stiffness of a cylindrical roller bearing with corrected roller generator | |
| Yang et al. | Reliability Test Rig of the Motorized Spindle and Improvements on Its Ability for High‐Speed and Long‐Term Tests | |
| Wu et al. | Nonlinear analysis of axial vibration of five-axis machine tool worktable with double turntable | |
| Li et al. | Effects of Velocity on Elastic Deformation in Ball Screw Drives and its Compensation | |
| Liu et al. | Timoshenko beam-based stability and natural frequency analysis for heavy load mechanical spindles |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20111109 Termination date: 20130315 |