CN103063432B - Machine tool mainshaft bearing configuration experimental apparatus for capability - Google Patents
Machine tool mainshaft bearing configuration experimental apparatus for capability Download PDFInfo
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Abstract
The invention provides a kind of machine tool mainshaft bearing configuration experimental apparatus for capability, comprising: cast iron base, experiment spindle assemblies, measured bearing; Experiment spindle assemblies comprises short spacer ring and outer short spacer ring, set nut in bearing seat, experiment main shaft, accurate interior long spacer ring and foreign minister's spacer ring, precision; Multiple measured bearing is arranged on experiment main shaft.The present invention is by changing setting element on bearing and axle, realize the configuration mode that rolling bearing different number, different directions and different span commonly used by main shaft, axial load, radial load is applied at spindle nose, the vibration of the different rotating accuracy of Bearing configuration lower main axis, the temperature rise of bearing and bearing can be tested, produce excitation at axle head setting-up eccentricity mass, the dynamic perfromance of axis system can be recorded.
Description
Technical field
The invention belongs to the test research device of machine tool mainshaft bearing configuration to main shaft performance impact, relate to that a kind of bearing variable number, installation direction are variable, the vibration acceleration of the machine tool chief axis of bearing position changeable on axle and monitoring main shaft, main shaft radial displacement, axial displacement, bear vibration acceleration, bearing temperature and spindle rotation accuracy characteristic experimental provision.
Background technology
Rolling bearing is the crucial support unit of Modern NC Machine Tool main shaft inner most general, in actual applications, rolling bearing by various different group mode, to adapt to various different machine tool applications.The grinding machine narrower to speed variation, optimum spindle design can be obtained for its specific speed, temperature, rigidity and life requirements, select suitable bearing arrangement and optimal cross section parameter, and for the very wide lathe of the large applicable surfaces of the range of work such as numerically controlled lathe, milling machine and machining center, the speed of mainshaft, rigidity will be different with requirement on machining accuracy, some requires or even conflicting, thus the selection of bearing can only require after Comprehensive Assessment according to machining precision, rigidity, load and life-span etc. fixed again.Therefore, adopt effective experimental technique Measurement accuracy under different bearing collocation form, the rigidity of main shaft, the performance such as rotating accuracy and temperature rise, analyze the type of bearing, number, direction and the position on axle to the affecting laws of main shaft performance, and then the military service performance tool of the rationality and main shaft that improve Bearing configuration design is of great significance.
Traditional main shaft performance test, often only for the main shaft of ad hoc structure, the collocation form of experimentation centre bearer is constant, cannot obtain the performance rule of different Bearing configuration, and bearing service manual also only provides Bearing configuration usable range qualitatively.For this reason, domestic and international many research and academic institution have carried out research with regard to the impact of Bearing configuration on main shaft performance, as NoviSad company of Yugoslavia uses experiment and emulation mode to have studied the dynamic-static character of high-speed main spindle, and investigate emphatically front support bearing arrangement mode to the impact of main shaft characteristic, the IgorZverv of the state-run polytechnical university in Moscow has carried out theoretical modeling to the main shaft of different Bearing configuration, the Hongqi.Li of Purdue University devises simple two bearings supporting spindle, investigates the configuration direction of bearing to the impact of main axle structure natural frequency.But simple investigation two block bearing configuration direction, on the impact of main shaft natural frequency, effectively can not obtain the affecting laws of Bearing configuration to main shaft combination property, also just cannot meet requirement main shaft being carried out to scientific design more.Although each famous bearing products manufacturer gives the qualitative description of not Bearing configuration, as high rigidity, high rotating speed, low temperature life etc., do not have the description of how concrete quantification, main shaft bearing configuration still lacks quantitative design guidance.Therefore, develop the experiment table that the performance that can configure multiple rolling bearing carries out Static and dynamic performance and testing temperature rising characteristic, further investigation is carried out to various configuration and is necessary.
Summary of the invention
The invention provides a kind of machine tool mainshaft bearing configuration experimental apparatus for capability, by changing setting element on the configuration of bearing and axle, realize the configuration mode of main shaft bearing different number, different directions and different span, constant axial load, radial load is applied at axle head, the rotating accuracy of different Bearing configuration lower main axis, axial displacement, radial displacement, the temperature rise of bearing and the vibration of bearing can be obtained, produce excitation at axle head setting-up eccentricity mass, the dynamic perfromance of axis system can be recorded.
For achieving the above object, the present invention is achieved by the following technical solutions.
A kind of machine tool mainshaft bearing configuration experimental apparatus for capability, comprise spindle drum and be arranged on the experiment main shaft in spindle drum, described experiment main shaft is provided with and organizes measured bearing more, by the first spacer ring isolation between described adjacent measured bearing group, by the second spacer ring isolation between described measured bearing group, by the combination of long spacer ring and short spacer ring, realize the change of measured bearing span, under realizing different Bearing configuration with this, the test of main shaft performance.
As the preferred embodiments of the present invention, described first spacer ring comprises the first outer ring spacer and the first cone spacer, and described second spacer ring comprises the second outer ring spacer and the second cone spacer, and the width of described second spacer ring is consistent with the width of measured bearing.
As the preferred embodiments of the present invention, described experimental provision includes axial test wrapper and adjustment spacer ring further, described axial test wrapper is as axial displacement test benchmark part, described test wrapper compression axis under the effect of front end set nut holds inner ring, the front end end cover be arranged on spindle drum compresses adjustment spacer ring, adjustment spacer ring compression axis bearing outer-ring.
As the preferred embodiments of the present invention, described experiment main shaft has former and later two supporting sections, each supporting section is installed one group of measured bearing, and the diameter of test main shaft between described two supporting sections is slightly less than the diameter of the test main shaft of former and later two supporting sections.
As the preferred embodiments of the present invention, the equal diameters of described former and later two supporting sections of experiment main shaft.
As the preferred embodiments of the present invention, between described measured bearing and spindle drum, be provided with cooling jacket, be connected by screw between described cooling jacket and spindle drum.
As the preferred embodiments of the present invention, described cooling jacket inwall has the groove of different length vertically, and this groove is corresponding with the quantity location of equal of bearing to be measured, and is uniformly distributed in radial direction, mounting temperature sensor in described groove.
As the preferred embodiments of the present invention, be coated with heat conductive silica gel in described temperature sensor mounted groove to reduce the space between groove and bearing.
As the preferred embodiments of the present invention, described experimental provision has shaft position sensor, radial displacement transducer further, and bear vibration sensor, described shaft position sensor and radial displacement transducer are arranged on front end end cover, described bear vibration sensor is arranged on the outer face of the measured bearing of outermost end, wire is extracted by the chilled water between measured bearing and spindle drum, measure main shaft run-out by radial displacement transducer, measured the axial runout of main shaft by shaft position sensor.
As the preferred embodiments of the present invention, described front-end of spindle is provided with load-on module, and described load-on module is load sleeve or eccentric massblock.
Compared with prior art, machine tool mainshaft bearing configuration experimental apparatus for capability of the present invention at least has the following advantages: the mode that the present invention adopts length spacer ring to combine, realizes the different Bearing configuration of main shaft bearing.
Accompanying drawing explanation
Fig. 1 is the main structure figure of a kind of embodiment of experimental provision of the present invention.
The layout of Fig. 2 temperature sensor of the present invention.
The layout of Fig. 3 acceleration transducer of the present invention, wherein Fig. 3 (a) is side view, and Fig. 3 (b) is vertical view.
The distributed architecture figure of Fig. 4 displacement transducer of the present invention, wherein, Fig. 4 (a) is side view, and Fig. 4 (b) is vertical view.
Fig. 5 (a) to Fig. 5 (c) is identical long spacer ring, the experimental program figure that number of bearings is different, wherein, Fig. 5 (a) for each bearing in front and back, Fig. 5 (b) be two, front end bearing, one, rear end bearing, Fig. 5 (c) is equal two bearings in front-end and back-end.
With or without the structural drawing of short spacer ring between Fig. 6 bearing.
Fig. 7 (1a) to Fig. 7 (5a) is number of bearings difference, the schematic structure diagram that direction is different, wherein, the structural drawing that Fig. 7 (1a) configures for bearings D B, the structural drawing that Fig. 7 (1b) configures for bearings D F, Fig. 7 (2a) and Fig. 7 (2b) is the structural drawing of three Bearing configuration, Fig. 7 (3a) is for the series connection of two, front end bearing and rear end two bearings and the structural drawing of configuration face-to-face, Fig. 7 (3b) is for two, front end bearing and two, rear end bearing and front end bearing and rear end bearing are the structural drawing of DF configuration, Fig. 7 (3c) is for two, front end bearing and two, rear end bearing and front end bearing and rear end bearing are the structural drawing of DB configuration, Fig. 7 (4a) is two, bearing rear end, three, front end bearing, and front end bearing is TT configuration, rear end bearing is the structural drawing of DT configuration, Fig. 7 (4b) is two, bearing rear end, three, front end bearing, and front end bearing is TBT configuration, rear end bearing is the structural drawing of DB configuration, Fig. 7 (5a) is two, bearing rear end, four, front end bearing, and front end bearing is QBC configuration, rear end bearing is the structural drawing of DB configuration.
The experimental program structural drawing that Fig. 8 (a) to Fig. 8 (c) is dissimilar Bearing configuration, wherein, Fig. 8 (a) for front end bearing be DB configuration, rear end bearing is single row roller bearing, Fig. 8 (b) for front end bearing be TBT configuration, rear end bearing is Biserial cylindrical roller bearing, Fig. 8 (c) for front end bearing be Biserial cylindrical roller bearing and bidirectional propulsion angle angular contact ball bearing, rear end bearing is Biserial cylindrical roller bearing.
Fig. 9 (a) and Fig. 9 (b) is the experimental program structural drawing of two kinds of different spans.
Reference numerals list in Fig. 1 to Fig. 9 is:
| 1 | Experiment main shaft | 2 | Front end end cover |
| 4 | Axial test wrapper | 5 | Cooling jacket |
| 8 | Adjustment spacer ring | 9 | Measured bearing |
| 10 | First outer ring spacer | 11 | First cone spacer |
| 12 | Spindle drum | 13 | Second outer ring spacer |
| 14 | Second cone spacer | 16 | Rear end cap |
| 18 | Shaft coupling | 19 | Cast iron base |
| 21 | Rear end set nut | 22 | Location spacer ring |
| 23 | Front end set nut | 25 | Loading place bearing |
| 26 | Load sleeve | 27 | Steel ball fixed head |
| 29 | Steel ball | A | Temperature sensor |
| B | Acceleration transducer | C | Radial displacement transducer |
| D | Shaft position sensor |
Embodiment
Below in conjunction with accompanying drawing, concrete introduction is done to machine tool mainshaft bearing configuration experimental apparatus for capability of the present invention:
Refer to shown in Fig. 1 to Fig. 4, experimental provision of the present invention comprises with lower module: cast iron base 19, drive electro spindle and servo drive system thereof and cooling system, experiment main shaft 1, spindle drum 12, axial loading system, radial loaded system and test macro, experiment main shaft 1 is fixed on cast iron base 19 by spindle drum 12, experiment main shaft 1 is provided with many group measured bearings 9, by the first spacer ring isolation between described adjacent measured bearing group, by the second spacer ring isolation between described measured bearing group, described first spacer ring comprises the first outer ring spacer 10 and the first cone spacer 11, described second spacer ring comprises the second outer ring spacer 13 and the second cone spacer 14, the width of described second spacer ring is consistent with the width of measured bearing 9, by the combination between the first spacer ring of different length and the second spacer ring, realize the change of Bearing configuration distance.
The front-end and back-end of described main shaft 1 are respectively arranged with front end end cover 2 and rear end cap 16, front end end cover 2 compresses adjustment spacer ring 8, adjustment spacer ring compresses bearing outer ring, the outer end of bearing inner race compresses the axial test wrapper 4 as axial displacement test benchmark part, described axial test wrapper is fastening by front end set nut 23, the rear end of described experiment main shaft is provided with rear end set nut 21, and described rear end set nut is pressed on bearing inner race by location spacer ring 22; Described axial displacement test benchmark part is arranged between front end bearing and front end set nut 23, by front end set nut 23, test benchmark and bearing can be axially fixed on main shaft simultaneously.
Described experiment main shaft 1 has former and later two supporting sections, each supporting section is installed one group of measured bearing, and the diameter of test main shaft between described two supporting sections is slightly less than the diameter (as axial displacement test benchmark part) of the test main shaft of former and later two supporting sections, the journal diameter of former and later two supporting sections is identical, ensures to install the internal diameter front and back bearings identical with external diameter 9.Described bearing pack is isolated by the first spacer ring, and pretension is provided, described bearing is axially fixed on experiment main shaft by front end set nut and rear end set nut, and described experiment spindle assemblies is overall with bearing saddle bore and rear end end face location, adopts front end end cover 2 to compress.
Cooling jacket 6 is provided with between described spindle drum 12 and measured bearing 9, be connected by screw between described cooling jacket 6 and spindle drum 12, described cooling jacket inwall has the groove A of different length vertically, this groove is corresponding with the quantity location of equal of bearing to be measured, and be uniformly distributed in radial direction, mounting temperature sensor in described groove, is coated with heat conductive silica gel to reduce the space between groove and bearing in temperature sensor mounted groove.
Described experimental provision has shaft position sensor, radial displacement transducer further, and bear vibration sensor, described shaft position sensor and radial displacement transducer are arranged on front end end cover, described bear vibration sensor is arranged on the outer face of the measured bearing of outermost end, wire is extracted by the chilled water between measured bearing and spindle drum, measure main shaft run-out by radial displacement transducer, measured the axial runout of main shaft by shaft position sensor.
Described front-end of spindle is provided with load-on module, described load-on module is load sleeve or eccentric massblock, described load sleeve 26 is arranged on experiment front-end of spindle by loading place bearing 25, axial hydraulic charger and hydraulic radial charger are fixed on cast iron base 19, axial force and radial force is applied, the characteristic of test permanent load lower main axis by charger; Available eccentric massblock replaces front-end of spindle load sleeve, carries out unbalance response test.Electro spindle is driven to be connected with experiment main shaft by shaft coupling.
When changing the configuration of bearing, first spindle assemblies entirety being shifted out from cooling jacket, by dismantling the set nut at two ends, realizing the increase of the number of the bearing in each bearing pack, reduce the dismantlement work in configuration variation process.
In the present invention, the type of measured bearing comprises internal diameter of the same race identical and angular contact ball bearing, single row roller bearing, Biserial cylindrical roller bearing, bidirectional angular contact thrust ball bearing that external diameter is identical; Load-on module is divided into constant force to load and eccentric mass loads two types.Constant force loads and is made up of load sleeve, axial hydraulic charger, hydraulic radial charger, there is steel ball 29 load sleeve end, steel ball 29 is fixed on load sleeve 26 by steel ball fixed head 27, is connected with main shaft radial through bearing, can ensure to load not hinder motion of main shaft simultaneously; Eccentric mass excitation is provided by eccentric mass dish.
Adopt machine tool mainshaft bearing of the present invention configuration experimental apparatus for capability can carry out the test of different bearing collocation form lower main axis performance, the implementation process of specific implementation difference configuration comprises the following steps:
1) refer to shown in Fig. 2, temperature sensor is installed in the preformed groove A of cooling jacket inside, and smear heat conductive silica gel by fill gaps, smooth for wire is glued in metallic channel;
2) refer to shown in Fig. 3, bearing acceleration microsensor pasted the outer face of front end outermost bearing, and leave standstill treat that it is cemented on bearing;
3) O-ring seal is installed, and cooling jacket is installed on bearing seat;
4) refer to shown in figure (5a), carry out the experiment of the first Bearing configuration, first location spacer ring 22 is installed on the ladder of testing main shaft also fastening with rear end set nut 21, then install successively the second cone spacer 13,14, bearing 9, first spacer ring of rear end 10,11, bearing 9, second spacer ring of front end 13,14, axial measuring basis part, front end set nut 23, by bearing assembly integral installation in cooling jacket, reconditioning adjustment spacer ring 8, compresses with front end end cover 2.
5) refer to shown in Fig. 4, displacement transducer is installed to primary clearance front end end cover also regulating probe and tested surface.
6) main shaft in Fig. 5 (a) is carried out to the rotating accuracy test under different loads, different rotating speeds, the vibration-testing of spindle assemblies, bear vibration test, bearing temperature rise test;
7) refer to shown in Fig. 5 (b), carry out the experiment of the second configuration, on the basis of figure (5a), spindle assemblies entirety is shifted out from cooling jacket, dismounting front end set nut 23, and take off the second spacer ring 13,14, installing the second spacer ring 13,14 of another kind of length again, then increase by a row bearing 9(specifically, is exactly angular contact ball bearing), experiment main shaft, to measuring basis part 4 and by bearing locking, is installed to cooling jacket by installation shaft, reconditioning adjustment spacer ring, compress with front end end cover, and repeat step 5) and 6);
8) refer to shown in Fig. 5 (c), carry out the experiment of the third configuration, on the basis of Fig. 5 (b), spindle assemblies entirety is shifted out from cooling jacket, dismounting rear end set nut 21, and take off the second spacer ring 13,14, second spacer ring 13,14 of another kind of length is installed, increase a row bearing (specifically, being exactly angular contact ball bearing) again, location spacer ring 22 by bearing locking is installed, main shaft is installed to cooling jacket, reconditioning adjustment spacer ring, compresses with front end end cover, and repeats step 5) and 6);
9) refer to shown in Fig. 6, first fastening with rear end set nut 21 on ladder location spacer ring 22 being installed to main shaft, then install successively the second spacer ring 13,14, adjacent bearing 9, first spacer ring in two, rear end 10,11, arranged side by side and adjacent bearing 9, axial measuring basis part 4, the front end set nut 23 in two, front end, by bearing assembly integral installation in cooling jacket, reconditioning adjustment spacer ring, compress with front end end cover, repeat step 5) and 6), carry out not adding short spacer ring in the middle of when bearing is connected, compare with the configuration in Fig. 5 (c);
10) refer to shown in Fig. 7 (1a) and (1b), carry out bearings D B configuration and DF configuration experiment;
11) refer to shown in Fig. 7 (2a) and (2b), carry out three Bearing configuration experiments;
12) refer to shown in Fig. 7 (3a), (3b), (3c) and Fig. 6, carry out the experiment in the first two rear two Bearing configuration direction, in Fig. 7 (3a), the first two rear two bearing is connected respectively, integral face opposite configures, in Fig. 7 (3b), front and back bearings is DF configuration, in Fig. 7 (3c), front and back bearings is DB configuration, and in Fig. 6, the first two rear two bearing is connected respectively, overall back-to-back configuration;
13) refer to shown in Fig. 7 (4a), (4b), carry out the experiment in first three rear two Bearing configuration direction, in Fig. 7 (4a), front bearing TT configures, and rear bearing DT configures, overall back-to-back configuration, and in figure (4b), front bearing TBT configures, and rear bearing DB configures;
14) refer to shown in Fig. 7 (5a), carry out the experiment of two Bearing configuration after front four, front bearing QBC configures, and rear bearing DB configures;
15) refer to shown in Fig. 8, carry out the experiment of dissimilar Bearing configuration, in Fig. 8 (a), bearing is DB configuration above, rear bearing is single row roller bearing, in Fig. 8 (b), front bearing is TBT configuration, rear bearing is Biserial cylindrical roller bearing, and in Fig. 8 (c), front bearing is Biserial cylindrical roller bearing and bidirectional propulsion angle angular contact ball bearing, and rear bearing is Biserial cylindrical roller bearing;
16) refer to shown in Fig. 9, the length of the first spacer ring in the middle of changing, and coordinate with corresponding second spacer ring, the experiment of different bearing span can be carried out, the contrast of three kinds of spans can be carried out with the configuration of Fig. 7 (1a);
Machine tool mainshaft bearing configuration experimental apparatus for capability of the present invention adopts following critical piece:
Angular contact ball bearing bearing: select NSK7014A5TYNSUMP4, bearing bore diameter 70mm, external diameter 110mm, width 20mm, dynamic load rating 44.5KN, grease lubrication limit speed 11200rpm;
Single row roller bearing: select NSKN1014RSMRCC1P4, bearing bore diameter 70mm, external diameter 110mm, width 20mm, dynamic load rating 50.0KN, grease lubrication limit speed 9000rpm;
Biserial cylindrical roller bearing: select NSKNN3014TBCC1P4, bearing bore diameter 70mm, external diameter 110mm, width 30mm, dynamic load rating 97.5KN, grease lubrication limit speed 5600rpm;
Bidirectional angular contact thrust ball bearing: select NSK70TAC20X+LP5, bearing bore diameter 70mm, external diameter 110mm, width 48mm, dynamic load rating 49.5KN, grease lubrication limit speed 4300rpm.；
Shaft position sensor: ZA-210803-00-025-10-02, diameter of phi 8, range 2mm; Screw thread specification: M10*1; Shell length: 25mm; Side head outlet; Long without screw thread: 0; Cable length 1 meter; Without armouring; Development in science and technology company limited of zhuzhou,hunan Air China;
Shaft position sensor fore-lying device: ZA-210800-50-08-01-01,5 meters of systems; Power supply :+24Vdc; Export: 0-5V; Temperature: 0-70 ° of C; Mounting means: guide rails assembling; Development in science and technology company limited of zhuzhou,hunan Air China;
Radial displacement transducer: ZA-210803-00-025-10-02, diameter of phi 8, range 2mm; Screw thread specification: M10*1; Shell length: 25mm; Side head outlet; Long without screw thread: 0; Cable length 1 meter; Without armouring; Development in science and technology company limited of zhuzhou,hunan Air China;
Radial displacement transducer fore-lying device: ZA-210800-50-08-01-01,5 meters of systems; Power supply :+24Vdc; Export: 0-5V; Temperature: 0-70 ° of C; Mounting means: guide rails assembling; Development in science and technology company limited of zhuzhou,hunan Air China;
Temperature sensor: the encapsulation of STT-R-A1-B3-C10-D1-E3-F1-G1-H1-L1-PA-T3-W1-S0, STT-R series platinum resistance temperature sensor stainless steel casing, PT100, diameter 3mm, long 10mm, measurement range-50 ~ 200 °;
Bear vibration sensor: ADXL330, ADI company of the U.S.;
D/A converter: DAC0830 series, American National Instrument Semiconductor company.
Simultaneous data-acquisition: NIPCI-6143, America NI company;
Shielding screw end daughter board: NISCB-68, America NI company;
The foregoing is only one embodiment of the present invention, it not whole or unique embodiment, the conversion of those of ordinary skill in the art by reading instructions of the present invention to any equivalence that technical solution of the present invention is taked, is claim of the present invention and contains.
Claims (9)
1. a machine tool mainshaft bearing configuration experimental apparatus for capability, it is characterized in that: this experimental provision comprises spindle drum (12) and is arranged on the experiment main shaft (1) in spindle drum, described experiment main shaft is provided with and organizes measured bearing more, by the first spacer ring isolation between adjacent measured bearing group, by the second spacer ring isolation between described measured bearing group, by the combination of the first spacer ring and the second spacer ring, realize the change of measured bearing span, under realizing different Bearing configuration with this, the test of main shaft performance; Be provided with cooling jacket (6) between described measured bearing and spindle drum (12), be connected by screw between described cooling jacket (6) and spindle drum (12).
2. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 1, it is characterized in that: described first spacer ring comprises the first outer ring spacer and the first cone spacer, described second spacer ring comprises the second outer ring spacer and the second cone spacer, and the width of described second spacer ring is consistent with the width of measured bearing.
3. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 1 or 2, it is characterized in that: described experimental provision includes axial test wrapper (4) and adjustment spacer ring (8) further, described axial test wrapper (4) is as axial displacement test benchmark part, described test wrapper (4) compression axis under the effect of front end set nut (23) holds inner ring, the front end end cover (2) be arranged on spindle drum compresses adjustment spacer ring, adjustment spacer ring compression axis bearing outer-ring.
4. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 1, it is characterized in that: described experiment main shaft has former and later two supporting sections, each supporting section is installed one group of measured bearing, and the diameter of test main shaft between described two supporting sections is slightly less than the diameter of the test main shaft of former and later two supporting sections.
5. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 4, is characterized in that: the equal diameters of described former and later two supporting sections of experiment main shaft.
6. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 1, it is characterized in that: described cooling jacket inwall has the groove of different length vertically, this groove is corresponding with the quantity location of equal of bearing to be measured, and is uniformly distributed in radial direction, mounting temperature sensor in described groove.
7. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 6, is characterized in that: be coated with heat conductive silica gel in described temperature sensor mounted groove to reduce the space between groove and bearing.
8. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 3, it is characterized in that: described experimental provision has shaft position sensor further, radial displacement transducer, and bear vibration sensor, described shaft position sensor and radial displacement transducer are arranged on front end end cover (2), described bear vibration sensor is arranged on the outer face of the measured bearing of outermost end, wire is drawn by the cooling jacket (6) between measured bearing and spindle drum (12), main shaft run-out is measured by radial displacement transducer, the axial runout of main shaft is measured by shaft position sensor.
9. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 1, it is characterized in that: described front-end of spindle is provided with load-on module, described load-on module is load sleeve or eccentric massblock.
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| CN103063432A (en) | 2013-04-24 |
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