CN102866006B - Strong-generality comprehensive experiment table for testing dynamic and static properties of spindle system - Google Patents
Strong-generality comprehensive experiment table for testing dynamic and static properties of spindle system Download PDFInfo
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- CN102866006B CN102866006B CN201210349417.XA CN201210349417A CN102866006B CN 102866006 B CN102866006 B CN 102866006B CN 201210349417 A CN201210349417 A CN 201210349417A CN 102866006 B CN102866006 B CN 102866006B
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Abstract
The invention discloses a strong-generality comprehensive experiment table for testing dynamic and static properties of a spindle system. The experiment table mainly comprises a driving electric spindle module, a mechanical spindle module and a hydraulic loading module, wherein the mechanical spindle module comprises a spindle, a bearing, a bearing pedestal, a pre-tightening force self-adaptive adjustment device, a temperature sensor, a displacement sensor, a pressure sensor and an air-oil lubrication device. The pre-tightening force self-adaptive adjustment is completed by six evenly distributed piezoelectric actuators, so as to realize the accurate control of the pre-tightening force of an angular contact ball bearing in the spindle system. According to the experiment table, different bearing configuration manners and different lubrication manners can be used, so that the properties of the experiment table are greatly expanded. Through controlling the rotation speed of an electric spindle, property test data such as temperature rise, rigidity and the like of the spindle under different configuration and pre-tightening conditions can be obtained by using the temperature sensor, the displacement sensor and the pressure sensor.
Description
Technical field
The invention belongs to the performance test field of high-speed main shaft of machine tool, relate to a kind of axis system dynamic and static state performance test synthesis experiment table of highly versatile.
Background technology
The kinematic behavior of main shaft-bearing arrangement has great impact to lathe overall performance, but currently still lack accurately effective analytical approach, main dependence experimental formula is estimated or is reduced to permanent flexible member to calculate, and application condition is large, therefore needs to carry out a large amount of experiments to verify.
Existing bearing-axis system experiment table function singleness, a certain experiential function (bearing rigidity, life-span etc.) can only be tested, such as Tang Yun ice devises the experimental provision of rolling bearing, to the equivalent stiffness of ceramic bearing test (Tang Yunbing etc. high speed ceramic rolling bearing equivalent stiffness analyze with experiment [J]. aviation power journal, 1995) impact of bearing performance shaft cannot, be analyzed.Therefore, design a highly versatile, each factor of experiment card comprehensive experiment platform that axis system rigidity, temperature rise etc. are affected can be surveyed necessary.
Rolling bearing is as rotary support element, and its military service performance directly affects axis system dynamic performance.Adopt different Bearing configuration forms, different lubricating systems and different bearing pre-fastening technology all will affect axle system performance.According to machine tool type and uses thereof, such as low-speed heave-load or high speed high rigidity requirement etc., main shaft has different requirement to Bearing configuration.The lubricating system of bearing directly affects its maximum speed.Correlative study shows, rational rolling bearing pretightening power can be eliminated rolling bearing and manufacture the play in assembling process, significantly improves high-speed main spindle rigidity and running accuracy; The skidding of bearing ball revolution can be reduced simultaneously, eliminate gyroscopic effect, and then improve the heating situation of bearing, extend the service life of bearing.Current up-to-date bearing pre-tightened controlling technology eliminates traditional constant preload Technique and exists significantly not enough: during low speed, pretightning force is less than normal, and bearing rigidity is declined, and the ability of the anti-forced vibration of main shaft and autovibration is weak, thus causes machining precision to decline; During high speed, pretightning force is bigger than normal, and bearing temperature rise is aggravated, and constrains the high speed of main shaft.
Affect the many factors of main shaft-bearing system as known from the above, how to realize carrying out multinomial test on single experiment table, shorten the construction cycle, raise the efficiency, this is necessary.So the present invention devises a kind of scheme of axis system dynamic and static state performance test synthesis experiment table of highly versatile.
Summary of the invention
The object of the invention is: lack a kind of simple and effective experimental provision for current machine tool chief axis-bearing arrangement dynamic and static state performance test, obtain the related data of the condition lower main axis various aspects of performance such as different Bearing configuration, pretightning force, lubricating system.The invention provides a kind of axis system dynamic and static state performance test synthesis experiment table of highly versatile.
For achieving the above object, the present invention take following technical scheme give realize:
A kind of axis system dynamic and static state performance test synthesis experiment table of highly versatile, comprise main shaft, the bearing be arranged on main shaft, be arranged on left end cap on main shaft and right end cap, the pedestal cap be fixedly connected with left end cap and right end cap and the pretightning force adjusting gear be arranged between right end cap and bearing; Described experiment table includes displacement transducer and temperature sensor further, and institute's displacement sensors is arranged on described left end cap, and and have gap between bearing; Described temperature sensor respectively from axially and longitudinally with bearing touch in order to measure the temperature variation of bearing.
As the preferred embodiments of the present invention, described pretightning force adjusting gear comprises pressure transducer, piezo-activator and jacking block, and described pressure transducer compresses piezo-activator, and piezo-activator is by jacking block and bearing close contact;
As the preferred embodiments of the present invention, described pedestal cap and right end cap and pretightning force adjusting gear are respectively arranged with the mounting hole run through for temperature sensor, and described temperature sensor runs through pedestal cap and right end cap and pretightning force adjusting gear and bearing close contact respectively;
As the preferred embodiments of the present invention, described bearing comprises inner ring, outer ring, and is placed in the angular contact ball bearing between inner ring and outer ring;
As the preferred embodiments of the present invention, described experiment table includes oil-air lubrication passage and splash ring further, and described oil-air lubrication channel setting is on pedestal cap, and lubricating oil enters from oil-air lubrication passage and lubricates bearing through splash ring;
As the preferred embodiments of the present invention, on described main shaft, the length of bearings mounted part is three bearing widths;
As the preferred embodiments of the present invention, described bearing is supported by bearing base, and described bearing base adopts integral structure, makes bearings face, front and back end time processing shaping, to ensure the right alignment of front and back end.
The present invention compared with prior art, has the following advantages:
(1) the main shaft-bearing system experiment under multiple Bearing configuration form can be realized.
(2) this experiment table can dynamic conditioning bearing pre-fastening, verifies in different pretightning force condition lower bearing military service performance.
(3) can Real-Time Monitoring main shaft-bearing system pretightning force size, axial displacement and bearing temperature change.
(4) bearing seat of integration can ensure the right alignment that front and back end is installed, and ensures installation accuracy.
(5) by adjustment fine thread, the problem that cannot be applied to bearing outer ring end face after individual piezoelectric that piezoelectricity physical dimension error causes is installed can effectively be overcome.
Accompanying drawing explanation
Fig. 1 is the structural drawing of axis system dynamic and static state performance test synthesis experiment table of the present invention;
Fig. 2 is the structural drawing of axis system of the present invention;
Fig. 3 is the partial enlarged drawing located of drawing a circle in Fig. 2;
Fig. 4 is bearing radial temperature sensor arrangenent diagram;
Fig. 5 is the three-dimensional structure diagram of pretightning force dynamic adjusting device;
Fig. 6 is the front elevation of Fig. 5;
Fig. 7 is the cut-open view of Fig. 6 along B-B line;
Fig. 8 is the cut-open view of Fig. 6 along A-A line;
Fig. 9 is fine-pitch screw of the present invention adjustment piezoelectric actuator structure figure.
Embodiment
Below in conjunction with accompanying drawing, apparatus of the present invention are described in further detail:
The invention provides a kind of axis system dynamic and static state performance test synthesis experiment table of highly versatile, its structure, with reference to Fig. 1, comprising: drive electro spindle module 1, mechanical main shaft module 2, hydraulic loaded module 3; Mechanical main shaft module 2 structure is with reference to Fig. 2: main shaft 4 is arranged on bearing seat 14, main shaft second segment multidiameter is provided with successively angular contact ball bearing 7, inside race 8, splash ring 9, two bearings become to be installed in series (being provided with splash ring between two bearings with thinking that bearing provides lubricating oil), and are arranged on main shaft 4 by set nut 6 is fastening.Please consult especially shown in Fig. 3, specifically, described experiment table comprises main shaft 4, bearing seat 14, pedestal cap 22, left bearing end cap 25, right bearing end cap 15, pretightning force adjusting gear 16, described left end cap and right end cap are fixed on main shaft 4, described pedestal cap 22 is fixed with left bearing end cap and right bearing end cap respectively by securing member 23, between described left bearing end cap 25 and right bearing end cap 15, bearing is installed, this bearing is angular contact bearing 7, splash ring 9 is installed between pair of horns contact bearing, described pedestal cap 22 offers the grease channel passed through for lubricating oil, this grease channel communicates with splash ring, like this, lubricating oil enters into splash ring by grease channel, thus the angular contact bearing of both sides is lubricated, described bearing is arranged on main shaft by set nut.Two pairs, front and back end bearing integral becomes form back-to-back, and that is the pair of bearings of the pair of bearings of front end and rear end is in form back-to-back.
Refer to shown in Fig. 5 to Fig. 8, described pretightning force adjusting gear 16 comprises pressure transducer 27,6 piezo-activators 28, jacking block 29 and pressure transducer 27 uniform on it forms, and by adjustment fine-pitch screw 31 compaction pressure sensor 27, piezo-activator 28, jacking block 29, jacking block 29 is effectively contacted with bearing outer ring; Pedestal cap 22 is provided with grease channel 19; Rear end bearing flap is arranged 3 temperature sensors 19, becomes 45 degree and be uniformly distributed; On left end cap installation shaft to displacement transducer 26; Hydraulic loaded module 3 applies axial load and radial load by two hydraulic cylinder shaft.
This experiment table bearing 7 model is 7210CD/P4, Figure 2 shows that form back-to-back.By changing inside race 8, outer collar, other Bearing configuration forms can be formed, to meet different request for utilizations (as low-speed heave-load, high speed etc.).Using piezo-activator 28 to carry out bearing pre-tightened, by controlling the power output of each actuator, thus realizing the dynamic conditioning of pretightning force, and auxiliary pressure sensor 28, directly can obtain accurate pretension force value.Bearing lubrication can use grease lubrication, if require to test under very high speed conditions, splash ring 9 and grease channel 20 also can be used to carry out oil spray lubrication.
Experimentally condition selectes Bearing configuration form, as shown in Figure 2, is that two pairs of bearings are installed back-to-back.Front support is followed successively by set nut 6, bearing 7, inside race 8, splash ring 9, bearing 7, outer collar 11; Rear end supports and is followed successively by pretightning force dynamic adjusting device 16, bearing 7, inner sleeve 8, splash ring 9, bearing 7, set nut 6; Pretightning force adjusting gear 16 is made up of pressure transducer 27,6 piezo-activators 28, jacking block 29 and pressure transducer 27 uniform on it, and the loading end of piezo-activator 28 is contacted with bearing 7 outer ring by jacking block 29, then is fixed on bearing seat by end cap; As shown in Figure 4, rear end bearing flap is installed the first temperature sensor 19, and on pressure transducer 27 also uniform 6 the second temperature sensor 17, second temperature sensors 17 and the first temperature sensor 19 all and bearing touch, to measure the temperature field information of axle system; On end cap installation shaft to displacement transducer 26, being used for Real-Time Monitoring axle-system axial beats; Finally mechanical main shaft module 2 left end first paragraph multidiameter being connected with driving electro spindle module 1 by shaft coupling, by controlling the output speed driving electro spindle module 1, realizing the adjustment of rotational speed of experiment table.Piezo-activator 28 loading end promotes the outer ring of bearing 7 left by jacking block 29, make bearing 7 inner ring to left movement, make axle 4 to left movement by inside race 8, splash ring 9, set nut 6 again, thus realize pretension by the set nut 6 of front end, inner sleeve 8, splash ring 9 pairs of front end pair of bearings 7.Six piezo-activators 28 adjust its output voltage by nonshared control unit and computer software, control the power output of each piezoelectric actuator, thus realize various pretightning force control technique.
Claims (7)
1. the axis system dynamic and static state performance test synthesis experiment table of a highly versatile, it is characterized in that: this experiment table comprises main shaft (4), the bearing be arranged on main shaft, is arranged on left end cap (25) on main shaft and right end cap (15), the pedestal cap be fixedly connected with left end cap and right end cap (22) and the pretightning force adjusting gear (16) be arranged between right end cap and bearing; Described experiment table includes displacement transducer (26) and temperature sensor (17,19) further, and institute's displacement sensors is arranged on described left end cap (25), and and have gap between bearing; Described temperature sensor respectively from axially and longitudinally with bearing touch in order to measure the temperature variation of bearing; Pretightning force adjusting gear (16) comprises pressure transducer (27), piezoelectric actuator (28) and jacking block (29), described pressure transducer compresses piezoelectric actuator, and piezoelectric actuator is by jacking block and bearing close contact; Described pedestal cap (22) and right end cap and pretightning force adjusting gear are respectively arranged with the mounting hole run through for temperature sensor, and described temperature sensor runs through pedestal cap (22) and right end cap and pretightning force adjusting gear and bearing close contact respectively.
2. the axis system dynamic and static state performance test synthesis experiment table of a kind of highly versatile as claimed in claim 1, is characterized in that: described bearing comprises inner ring, outer ring, and is placed in the angular contact ball bearing between inner ring and outer ring.
3. the axis system dynamic and static state performance test synthesis experiment table of a kind of highly versatile as claimed in claim 1, it is characterized in that: described experiment table includes oil-air lubrication passage (20) and splash ring (9) further, described oil-air lubrication passage (20) is arranged on pedestal cap (22), and lubricating oil enters from oil-air lubrication passage and lubricates bearing through splash ring.
4. the axis system dynamic and static state performance test synthesis experiment table of a kind of highly versatile as claimed in claim 1, is characterized in that: on described main shaft, the length of bearings mounted part is three bearing widths.
5. the axis system dynamic and static state performance test synthesis experiment table of a kind of highly versatile as claimed in claim 1, it is characterized in that: described bearing is supported by bearing base (14), described bearing base (14) adopts integral structure, make bearings face, front and back end time processing shaping, to ensure the right alignment of front and back end.
6. the axis system dynamic and static state performance test synthesis experiment table of a kind of highly versatile as described in claim 1 or 3 or 4 or 5, is characterized in that: one end of described main shaft is connected with and drives electro spindle module to operate in order to drive shaft (4).
7. the axis system dynamic and static state performance test synthesis experiment table of a kind of highly versatile as claimed in claim 6, is characterized in that: described experiment table includes hydraulic loaded module further in order to apply axis and radial load to main shaft (4).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210349417.XA CN102866006B (en) | 2012-09-19 | 2012-09-19 | Strong-generality comprehensive experiment table for testing dynamic and static properties of spindle system |
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| CN201210349417.XA CN102866006B (en) | 2012-09-19 | 2012-09-19 | Strong-generality comprehensive experiment table for testing dynamic and static properties of spindle system |
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| CN102866006B true CN102866006B (en) | 2015-01-21 |
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| CN103837339B (en) * | 2014-03-26 | 2016-03-09 | 中国工程物理研究院机械制造工艺研究所 | A kind of dynamic servo power-driven system |
| CN104792533B (en) * | 2015-04-29 | 2017-05-17 | 武汉理工大学 | Integrated testbed for numerical control machine spindle thermal error causes and test method |
| CN104880308B (en) * | 2015-05-27 | 2017-11-28 | 西安交通大学 | A kind of main shaft axial force isostatic pressed loading device |
| CN106482949A (en) * | 2015-08-25 | 2017-03-08 | 北京航天动力研究所 | Angular contact ball bearing radial direction Static stiffness measurement apparatus |
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| CN106896834B (en) * | 2016-11-07 | 2023-05-09 | 天津大学 | High-speed accurate main shaft pretightning force intelligent control test bench based on piezoelectric actuator |
| CN106908178B (en) * | 2016-11-07 | 2022-12-02 | 天津大学 | High-speed precision main shaft pretightening force test device and use method thereof |
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| CN113721044A (en) * | 2021-11-01 | 2021-11-30 | 杭州斯格尔液压机械有限公司 | High-speed large-torque main shaft of new energy motor test bench |
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