CN103063432A - Machine tool mainshaft bearing configuration performance experimental device - Google Patents
Machine tool mainshaft bearing configuration performance experimental device Download PDFInfo
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- CN103063432A CN103063432A CN2012104988995A CN201210498899A CN103063432A CN 103063432 A CN103063432 A CN 103063432A CN 2012104988995 A CN2012104988995 A CN 2012104988995A CN 201210498899 A CN201210498899 A CN 201210498899A CN 103063432 A CN103063432 A CN 103063432A
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Abstract
The invention provides a machine tool mainshaft bearing configuration performance experimental device which comprises a cast iron base, experimental mainshaft components, and detected bearings. The experimental mainshaft components comprise a bearing block, an experimental mainshaft, a precise inner long space ring and a precise outer long space ring, a precise inner short space ring and a precise outer short space ring and a locknut. A plurality of the detected bearings are arranged on the experimental mainshaft. Configuration methods of frequently-used antifriction bearings with different numbers, different directions and different spans of a mainshaft are achieved through changing bearings and setting elements on the mainshaft. Rotation accuracy of the mainshaft, temperature rising of the bearings and vibration of the bearings under different bearing configuration can be tested by adding thrust load and radial load to end portions of the mainshaft. Dynamic characteristics of mainshaft system can be obtained through excitation which is produced by installing eccentricity mass blocks on the end portions of the mainshaft.
Description
Technical field
The invention belongs to machine tool mainshaft bearing configuration to the test research device of main shaft performance impact, relate to that a kind of bearing number is variable, installation direction is variable, the experimental provision of vibration acceleration, main shaft radial displacement, axial displacement, bear vibration acceleration, bearing temperature and the spindle rotation accuracy characteristic of the machine tool chief axis of bearing position changeable on axle and monitoring main shaft.
Background technology
Rolling bearing is the crucial support unit of Modern NC Machine Tool main shaft inner most general, and in actual applications, rolling bearing can pass through various group mode, to adapt to various machine tool applications.The grinding machine narrower to the velocity variations scope, can obtain optimum spindle design for its specific speed, temperature, rigidity and life requirements, select suitable bearing arrangement and optimal cross section parameter, and for very wide lathes of the large applicable surface of the range of work such as numerically controlled lathe, milling machine and machining centers, the speed of mainshaft, rigidity will be different with requirement on machining accuracy, some requirement or even conflicting is so the selection of bearing can only require to decide after the Comprehensive Assessment according to machining precision, rigidity, load and life-span etc. again.Therefore, adopt effective experimental technique Measurement accuracy under different bearing collocation forms, the performances such as the rigidity of main shaft, rotating accuracy and temperature rise, analyze type, number, direction and the position on axle of bearing to the rule that affects of main shaft performance, and then the raising bearing configures the rationality of design and the military service performance tool of main shaft 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, can't obtain the performance rule of different bearing configurations, also only provides qualitatively bearing configuration usable range on the bearing service manual.For this reason, domestic and international many research and academic institution configure with regard to bearing research have been carried out in the impact of main shaft performance, use experiment and emulation mode to study the sound characteristic of high-speed main spindle such as Yugoslavia Novi Sad company, and investigate emphatically front support bearing arrangement mode to the impact of main shaft characteristic, the Igor Zverv of the state-run polytechnical university in Moscow has carried out theoretical modeling to the main shaft of different bearing configurations, the Hongqi.Li of Purdue University has designed 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 bearings configuration direction can not effectively obtain the bearing configuration to the rule that affects of main shaft combination property to the impact of main shaft natural frequency, also just can't satisfy main shaft is carried out the more requirement of science design.Although each famous bearing products manufacturer has provided the not qualitative description of bearing configuration, such as high rigidity, high rotating speed, low temperature life etc., there is not the description of how concrete quantification, the main shaft bearing configuration still lacks quantitative design guidance.Therefore, develop the experiment table that can carry out to the performance of multiple rolling bearing configuration quiet dynamic perfromance and testing temperature rising characteristic, various configurations are furtherd investigate be necessary.
Summary of the invention
The invention provides a kind of machine tool mainshaft bearing configuration experimental apparatus for capability, setting element on configuration by changing bearing and the axle, realize the configuration mode of the different numbers of main shaft bearing, different directions and different spans, apply constant axial load, radial load at axle head, can obtain rotating accuracy, axial displacement, radial displacement, the temperature rise of bearing and the vibration of bearing of different bearing configuration lower main axis, produce excitation at axle head setting-up eccentricity mass, can record the dynamic perfromance of axis system.
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 installed in the interior experiment main shaft of spindle drum, many group measured bearings are installed on the described experiment main shaft, isolate by the first spacer ring between the described adjacent measured bearing group, by the isolation of the second spacer ring, by the combination of long spacer ring and short spacer ring, realize the change of measured bearing span between the described measured bearing group, realize that with this different bearing configurations are lower, the main shaft performance test.
As the preferred embodiments of the present invention, described the first spacer ring comprises the first outer ring spacer and the first cone spacer, and described the second spacer ring comprises the second outer ring spacer and the second cone spacer, and the width of described the second spacer ring is consistent with the width of measured bearing.
As the preferred embodiments of the present invention, described experimental provision further includes axial test wrapper and adjusts spacer ring, 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 that is installed on the spindle drum compresses the adjustment spacer ring, adjusts 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, one group of measured bearing is installed on each supporting section, and the diameter of the 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, be provided with cooling jacket between described measured bearing and the spindle drum, be connected by screw between described cooling jacket and the 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 radially evenly distributing mounting temperature sensor in the described groove.
As the preferred embodiments of the present invention, be coated with heat conductive silica gel in the described temperature sensor mounted groove to reduce the space between groove and the bearing.
As the preferred embodiments of the present invention, described experimental provision further has shaft position sensor, radial displacement transducer, and bear vibration sensor, described shaft position sensor and radial displacement transducer are installed on the front end end cover, described bear vibration installation of sensors is in the outer face of the measured bearing of outermost end, wire is extracted by the chilled water between measured bearing and spindle drum, measure the diameter run-out of main shaft by radial displacement transducer, measure the axial runout of main shaft by shaft position sensor.
As the preferred embodiments of the present invention, described front-end of spindle is equipped 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 has the following advantages at least: the present invention adopts the mode of length spacer ring combination, realizes the different bearing configurations of main shaft bearing.
Description of drawings
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, 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, Fig. 4 (b) is vertical view.
Fig. 5 (a) is identical long spacer ring to Fig. 5 (c), the experimental program figure that number of bearings is different, and wherein, Fig. 5 (a) is each bearing of front and back, and Fig. 5 (b) is two bearings of front end, and the bearing in rear end, Fig. 5 (c) they are equal two bearings in front-end and back-end.
The structural drawing that has or not short spacer ring between Fig. 6 bearing.
Fig. 7 (1a) is that number of bearings is different to Fig. 7 (5a), the schematic structure diagram that direction is different, wherein, Fig. 7 (1a) is the structural drawing of bearings D B configuration, Fig. 7 (1b) is the structural drawing of bearings D F configuration, Fig. 7 (2a) and Fig. 7 (2b) are the structural drawing of three bearing configurations, Fig. 7 (3a) is the structural drawing of two bearing series connection of two bearings of front end and rear end and face-to-face configuration, Fig. 7 (3b) is the structural drawing of DF configuration for two bearings of two bearings of front end and rear end and front end bearing and rear end bearing, Fig. 7 (3c) is the structural drawing of DB configuration for two bearings of two bearings of front end and rear end and front end bearing and rear end bearing, Fig. 7 (4a) is two bearings in three bearing rear ends of front end, and front end bearing is the TT configuration, rear end bearing is the structural drawing of DT configuration, Fig. 7 (4b) is two bearings in three bearing rear ends of front end, and front end bearing is the TBT configuration, rear end bearing is the structural drawing of DB configuration, Fig. 7 (5a) is two bearings in four bearing rear ends of front end, and front end bearing is the QBC configuration, and rear end bearing is the structural drawing of DB configuration.
Fig. 8 (a) is the experimental program structural drawing of dissimilar bearing configuration to Fig. 8 (c), wherein, Fig. 8 (a) is the DB configuration for front end bearing, rear end bearing is single row roller bearing, Fig. 8 (b) is the TBT configuration for front end bearing, rear end bearing is Biserial cylindrical roller bearing, and Fig. 8 (c) is Biserial cylindrical roller bearing and bidirectional propulsion angle angular contact ball bearing for front end bearing, and rear end bearing is Biserial cylindrical roller bearing.
Fig. 9 (a) is the experimental program structural drawing of two kinds of different spans with Fig. 9 (b).
Reference numerals list among Fig. 1 to Fig. 9 is:
| 1 | The experiment main shaft | 2 | Front end end cover |
| 4 | Axial test wrapper | 5 | Cooling jacket |
| 8 | Adjust |
9 | Measured bearing |
| 10 | The first |
11 | The first cone spacer |
| 12 | |
13 | The second |
| 14 | The |
16 | |
| 18 | Shaft coupling | 19 | |
| 21 | The rear end set |
22 | The location spacer ring |
| 23 | The front end set nut | 25 | Loading place bearing |
| 26 | Load sleeve | 27 | The 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 machine tool mainshaft bearing configuration experimental apparatus for capability of the present invention is done concrete the introduction:
See also Fig. 1 to shown in Figure 4, experimental provision of the present invention comprises with lower module: cast iron base 19, drive electric main shaft 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 the cast iron base 19 by spindle drum 12, many group measured bearings 9 are installed on the experiment main shaft 1, isolate by the first spacer ring between the described adjacent measured bearing group, isolate by the second spacer ring between the described measured bearing group, described the first spacer ring comprises the first outer ring spacer 10 and the first cone spacer 11, and described the second spacer ring comprises the second outer ring spacer 13 and the second cone spacer 14, and the width of described the second spacer ring is consistent with the width of measured bearing 9, by the first spacer ring of different length and the combination between 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 adjusts spacer ring 8, adjust spacer ring and compress 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 equipped 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 installed between front end bearing and the front end set nut 23, by front end set nut 23, test benchmark and bearing can be axially fixed on the main shaft simultaneously.
Described experiment main shaft 1 has former and later two supporting sections, one group of measured bearing is installed on each supporting section, and the diameter of the 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 axle journal diameter of former and later two supporting sections is identical, and assurance can be installed the internal diameter front and back bearings identical with external diameter 9.Described bearing pack is isolated by the first spacer ring, and provide pretension, described bearing is axially fixed on the experiment main shaft by front end set nut and rear end set nut, and described experiment spindle assemblies integral body adopts front end end cover 2 to compress with bearing saddle bore and rear end end face location.
Be provided with cooling jacket 6 between described spindle drum 12 and the measured bearing 9, be connected by screw between described cooling jacket 6 and the 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 radially evenly distributing, mounting temperature sensor in the described groove is coated with heat conductive silica gel to reduce the space between groove and the bearing in the temperature sensor mounted groove.
Described experimental provision further has shaft position sensor, radial displacement transducer, and bear vibration sensor, described shaft position sensor and radial displacement transducer are installed on the front end end cover, described bear vibration installation of sensors is in the outer face of the measured bearing of outermost end, wire is extracted by the chilled water between measured bearing and spindle drum, measure the diameter run-out of main shaft by radial displacement transducer, measure the axial runout of main shaft by shaft position sensor.
Described front-end of spindle is equipped with load-on module, described load-on module is load sleeve or eccentric massblock, described load sleeve 26 is installed in the experiment front-end of spindle by loading place bearing 25, axial hydraulic charger and hydraulic radial charger are fixed on the cast iron base 19, apply axial force and radial force by charger, the characteristic of test permanent load lower main axis; Available eccentric massblock replaces the front-end of spindle load sleeve, carries out the unbalance response test.Driving electric main shaft links to each other with the experiment main shaft by shaft coupling.
When changing the configuration of bearing, first spindle assemblies integral body is shifted out from cooling jacket, by the set nut at dismounting two ends, realize the increase of the number of the bearing in each bearing pack, reduce the dismantlement work in the configuration variation process.
In the present invention, the type of measured bearing comprises angular contact ball bearing, single row roller bearing, Biserial cylindrical roller bearing, the bidirectional angular contact thrust ball bearing that internal diameter of the same race is identical and external diameter is identical; Load-on module is divided into the constant force loading and eccentric mass loads two types.Constant force loads and is comprised of load sleeve, axial hydraulic charger, hydraulic radial charger, there is steel ball 29 the load sleeve end, steel ball 29 is fixed on the load sleeve 26 by steel ball fixed head 27, radially is connected with main shaft by bearing, can guarantee that loading does not hinder motion of main shaft simultaneously; The eccentric mass excitation is provided by the eccentric mass dish.
Adopt machine tool mainshaft bearing configuration experimental apparatus for capability of the present invention can carry out different bearing collocation form lower main axis performance tests, the implementation process of the different configurations of specific implementation comprises the following steps:
1) sees also shown in Figure 2ly, temperature sensor is installed in the preformed groove A of cooling jacket inside, and smears heat conductive silica gel the space is filled, with smooth being glued in the metallic channel of wire;
2) see also shown in Figure 3ly, the bearing acceleration microsensor is pasted the outer face of front end outermost bearing, and leave standstill and treat that it is cemented on the bearing;
3) O-ring seal is installed, and cooling jacket is installed on the bearing seat;
4) see also shown in the figure (5a), carry out the experiment of the first bearing configuration, at first will locate spacer ring 22 is installed on the ladder of testing main shaft also fastening with rear end set nut 21, then bearing 9, the first spacer ring 10,11, the bearing 9 of front end, the second spacer ring 13,14, axial measuring basis part, the front end set nut 23 of the second cone spacer 13,14, rear end are installed successively, with the bearing assembly integral installation in cooling jacket, spacer ring 8 is adjusted in reconditioning, compresses with front end end cover 2.
5) see also shown in Figure 4, the primary clearance that displacement transducer is installed on the front end end cover and regulates probe and tested surface.
6) the rotating accuracy test, the vibration-testing of spindle assemblies, bear vibration test, the bearing temperature rise that the main shaft among Fig. 5 (a) are carried out under different loads, the different rotating speeds are tested;
7) see also shown in Fig. 5 (b), carry out the experiment of the second configuration, on the basis of figure (5a), spindle assemblies integral body is shifted out from cooling jacket, dismounting front end set nut 23, and take off the second spacer ring 13,14, second spacer ring 13,14 of another kind of length being installed again, being increased by a row bearing 9(specifically again, is exactly angular contact ball bearing), installation shaft will be tested main shaft and be installed to cooling jacket to measuring basis part 4 and with bearing locking, and spacer ring is adjusted in reconditioning, compress with front end end cover, and repeat step 5) and 6);
8) see also shown in Fig. 5 (c), carry out the experiment of the third configuration, on the basis of Fig. 5 (b), spindle assemblies integral body 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 again a row bearing (specifically, being exactly angular contact ball bearing), location spacer ring 22 is installed and with bearing locking, main shaft is installed to cooling jacket, spacer ring is adjusted in reconditioning, compresses with front end end cover, and repeats step 5) and 6);
9) see also shown in Figure 6, to locate at first that spacer ring 22 is installed on the ladder of main shaft and fastening with rear end set nut 21, then the second spacer ring 13,14, two the adjacent bearings 9 in rear end, the first spacer ring 10,11, two arranged side by side and adjacent bearings 9 of front end, axial measuring basis part 4, front end set nut 23 are installed successively, with the bearing assembly integral installation in cooling jacket, spacer ring is adjusted in reconditioning, compress with front end end cover, repeating step 5) and 6), carry out not adding short spacer ring in the middle of bearing when series connection, compare with configuration among Fig. 5 (c);
10) see also Fig. 7 (1a) and (1b) shown in, carry out bearings D B configuration and DF configuration and test;
11) see also Fig. 7 (2a) and (2b) shown in, carry out three bearings configuration experiment;
12) see also Fig. 7 (3a), (3b), (3c) and shown in Figure 6, carry out the experiment of the first two rear two bearings configuration direction, the first two rear two bearing is connected respectively among Fig. 7 (3a), the configuration of integral face opposite, front and back bearings is the DF configuration among Fig. 7 (3b), front and back bearings is the DB configuration among Fig. 7 (3c), and the first two rear two bearing is connected respectively whole back-to-back configuration among Fig. 6;
13) see also shown in Fig. 7 (4a), (4b), carry out the experiment of first three rear two bearings configuration direction, front bearing TT configuration among Fig. 7 (4a), rear bearing DT configuration, front bearing TBT configuration in (4b) is schemed in whole back-to-back configuration, rear bearing DB configuration;
14) see also shown in Fig. 7 (5a), carry out the experiment of two bearings configuration after front four, front bearing QBC configuration, rear bearing DB configuration;
15) see also shown in Figure 8, carry out the experiment of dissimilar bearing configuration, spherical bearing is the DB configuration before among Fig. 8 (a), rear bearing is single row roller bearing, front bearing is the TBT configuration among Fig. 8 (b), rear bearing is Biserial cylindrical roller bearing, and front bearing is Biserial cylindrical roller bearing and bidirectional propulsion angle angular contact ball bearing among Fig. 8 (c), and rear bearing is Biserial cylindrical roller bearing;
16) see also shown in Figure 9ly, the length of the first spacer ring in the middle of changing, and cooperate with corresponding the second spacer ring can be carried out the experiment of different bearing spans, can carry out the contrast of three kinds of spans 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 NSK N1014RSMRCC1P4, bearing bore diameter 70mm, external diameter 110mm, width 20mm, dynamic load rating 50.0KN, grease lubrication limit speed 9000rpm;
Biserial cylindrical roller bearing: select NSK NN3014TBCC1P4, 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 NSK 70TAC20X+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; A side outlet; Long without screw thread: 0; 1 meter of cable length; 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 systems; Power supply :+24Vdc; Output: 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; A side outlet; Long without screw thread: 0; 1 meter of cable length; 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 systems; Power supply :+24Vdc; Output: 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: STT-R-A1-B3-C10-D1-E3-F1-G1-H1-L1-PA-T3-W1-S0, the encapsulation of STT-R series platinum resistance temperature sensor stainless steel casing, PT100, diameter 3mm, long 10mm, measurement range-50 ~ 200 °;
Bear vibration sensor: ADXL330, U.S. ADI company;
D/A converter: DAC0830 series, American National Instrument Semiconductor company.
Simultaneous data-acquisition: NI PCI-6143, America NI company;
Shielding screw end daughter board: NI SCB-68, America NI company;
The above only is one embodiment of the present invention, it or not whole or unique embodiment, the conversion of any equivalence that those of ordinary skills take technical solution of the present invention by reading instructions of the present invention is claim of the present invention and contains.
Claims (10)
1. a machine tool mainshaft bearing configures experimental apparatus for capability, it is characterized in that: this experimental provision comprises spindle drum (12) and is installed in the interior experiment main shaft (1) of spindle drum, many group measured bearings are installed on the described experiment main shaft, isolate by the first spacer ring between the described adjacent measured bearing group, isolate by the second spacer ring between the described measured bearing group, combination by the first spacer ring and the second spacer ring, realize the change of measured bearing span, realize that with this different bearing configurations are lower, the main shaft performance test.
2. a kind of machine tool mainshaft bearing as claimed in claim 1 configures experimental apparatus for capability, it is characterized in that: described the first spacer ring comprises the first outer ring spacer and the first cone spacer, described the second spacer ring comprises the second outer ring spacer and the second cone spacer, and the width of described the second spacer ring is consistent with the width of measured bearing.
3. a kind of machine tool mainshaft bearing as claimed in claim 1 or 2 configures experimental apparatus for capability, it is characterized in that: described experimental provision further includes axial test wrapper (4) and adjusts spacer ring (8), 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) that is installed on the spindle drum compresses the adjustment spacer ring, adjusts spacer ring compression axis bearing outer-ring.
4. a kind of machine tool mainshaft bearing as claimed in claim 1 configures experimental apparatus for capability, it is characterized in that: described experiment main shaft has former and later two supporting sections, one group of measured bearing is installed on each supporting section, and the diameter of the 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 as claimed in claim 1 configures experimental apparatus for capability, it is characterized in that: be provided with cooling jacket (6) between described measured bearing and the spindle drum (12), be connected by screw between described cooling jacket (6) and the spindle drum (12).
7. a kind of machine tool mainshaft bearing as claimed in claim 6 configures experimental apparatus for capability, 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 radially evenly distributing mounting temperature sensor in the described groove.
8. a kind of machine tool mainshaft bearing configuration experimental apparatus for capability as claimed in claim 7 is characterized in that: be coated with heat conductive silica gel in the described temperature sensor mounted groove to reduce the space between groove and the bearing.
9. a kind of machine tool mainshaft bearing as claimed in claim 3 configures experimental apparatus for capability, it is characterized in that: described experimental provision further has shaft position sensor, radial displacement transducer, and bear vibration sensor, described shaft position sensor and radial displacement transducer are installed on the front end end cover (2), described bear vibration installation of sensors is in the outer face of the measured bearing of outermost end, wire is drawn by the cooling jacket (6) between measured bearing and the spindle drum (12), measure the diameter run-out of main shaft by radial displacement transducer, measure the axial runout of main shaft by shaft position sensor.
10. a kind of machine tool mainshaft bearing as claimed in claim 1 configures experimental apparatus for capability, and it is characterized in that: described front-end of spindle is equipped with load-on module, and described load-on module is load sleeve or eccentric massblock.
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| CN110207834A (en) * | 2019-05-22 | 2019-09-06 | 浙江优特轴承有限公司 | For detecting the location structure of main shaft bearing Internal and external cycle temperature |
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