CN109765015B - Method and device for testing radial dynamic stiffness of main shaft - Google Patents
Method and device for testing radial dynamic stiffness of main shaft Download PDFInfo
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- CN109765015B CN109765015B CN201811556862.7A CN201811556862A CN109765015B CN 109765015 B CN109765015 B CN 109765015B CN 201811556862 A CN201811556862 A CN 201811556862A CN 109765015 B CN109765015 B CN 109765015B
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Abstract
The invention discloses a method for testing radial dynamic stiffness of a main shaft, which comprises the following steps: fixed outside the main shaftSleeving a bearing plate; sleeving a hydrostatic bearing clearance outside the bearing plate, wherein two oil cavities are formed in the hydrostatic bearing; arranging the two oil cavities along the radial direction of the main shaft and oppositely arranging the two oil cavities in the radial direction; the initial gaps between the end surfaces of the two oil cavities where the cavities are located and the bearing plate are the same in size; testing the radial displacement of the bearing plate by using a displacement sensor, and determining the radial displacement x of the main shaft according to the radial displacement of the bearing plate; calculating the effective bearing area S of an oil cavity of the hydrostatic bearing; calculating the oil discharge hydraulic resistance R of the oil cavity of the hydrostatic bearing0(ii) a And calculating the radial dynamic stiffness k applied to the main shaft. The invention can reduce vibration and avoid safety accidents caused by collision and abrasion. The invention also discloses a radial dynamic stiffness testing device of the main shaft.
Description
Technical Field
The invention relates to the technical field of main shafts, in particular to a method and a device for testing radial dynamic stiffness of a main shaft.
Background
At present, a main shaft of a high-speed machine tool is a core functional component of a modern machine tool, and the main shaft of the high-speed machine tool is used for driving a cutter (a grinding wheel) or a workpiece to rotate so as to realize high-speed precision machining. Along with the continuous improvement of the requirements of modern industry on the machining precision and the machining efficiency of the machine tool, the requirements of the machine tool on the performance of the main shaft are higher and higher. The rigidity is one of the important indexes for measuring the performance of the main shaft of the high-speed machine tool. The rigidity of the main shaft comprises static rigidity in a static state and dynamic rigidity in high-speed operation. The rigidity testing method which is feasible in engineering and widely adopted at present is a static rigidity testing method. However, the static stiffness cannot truly reflect the deformation resistance of the spindle under the condition of bearing cutting load during high-speed operation, and only the dynamic stiffness can scientifically reflect the dynamic bearing characteristic of the spindle.
The prior dynamic stiffness testing method in engineering comprises the following steps: the rolling bearing type loading measurement method is characterized in that a rolling bearing is directly used as a loading bearing, and the excircle of the loading bearing is contacted with the excircle of a main shaft overhanging end, so that the main shaft is loaded; however, this approach has the following drawbacks:
(1) the loading bearing rotates at a high speed along with the main shaft, so that the noise is high and the vibration is large;
(2) the loading bearing is in smooth normal contact with the excircle of the main shaft, so that the loading bearing is easy to damage due to heat generated by collision and grinding.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to provide a radial dynamic stiffness testing method of a main shaft, and the invention aims to provide a radial dynamic stiffness testing device of the main shaft, which adopts a hydrostatic bearing arranged in a gap to realize loading, and a gap exists between the hydrostatic bearing and a bearing plate, so that the vibration can be reduced, and safety accidents caused by collision and abrasion can be avoided.
One of the purposes of the invention is realized by adopting the following technical scheme:
a radial dynamic stiffness testing method of a main shaft comprises the following steps:
the preparation method comprises the following steps: a bearing plate is fixedly sleeved outside the main shaft; sleeving a hydrostatic bearing clearance outside the bearing plate, wherein two oil cavities are formed in the hydrostatic bearing; arranging the two oil cavities along the radial direction of the main shaft and oppositely arranging the two oil cavities in the radial direction; the initial gaps between the end surfaces of the two oil cavities where the cavities are located and the bearing plate are the same in size;
and a load applying step: driving the main shaft to rotate; two constant delivery pumps are adopted to respectively and correspondingly input oil into the two oil cavities, and the oil is sprayed through the oil cavitiesTowards the carrier plate; at the same time, the rotating speed V of one of the constant delivery pumps is adjusted1Is adjusted to n0+nxAnd the rotational speed V of the other fixed displacement pump is adjusted2Is adjusted to n0-nx；
A radial displacement acquisition step: in the step of applying the load, a displacement sensor is adopted to test the radial displacement of the bearing plate, and the radial displacement x of the main shaft is determined according to the radial displacement of the bearing plate;
a calculation step:
calculating the effective bearing area S of the oil cavity according to an area calculation formula;
calculating the oil discharge resistance R of the oil cavity0；
Calculating the radial dynamic stiffness k of the main shaft according to the formula (1);
wherein, in the above formula (1):
x is the radial displacement of the spindle; s is the effective bearing area; n is0The rated rotating speed of the fixed displacement pump; n isxIs the rotational speed V1Or speed of rotation V2A variation amount with respect to the rated rotation speed; q. q.s0The rated oil quantity pumped out by the fixed displacement pump every time the fixed displacement pump rotates one circle; r0The oil outlet liquid resistance is set; h is0Is the initial gap size.
Further, in the radial displacement obtaining step, the two displacement sensors are used for testing the radial displacement of the bearing plate, and the average value of the values tested by the two displacement sensors is taken as the radial displacement x of the main shaft.
Further, in the step of applying the load, the current supplied to the fixed displacement pump is controlled by a frequency converter so as to adjust the rotating speed of the fixed displacement pump.
Further, a flange is used as the bearing plate.
The second purpose of the invention is realized by adopting the following technical scheme:
a radial dynamic stiffness testing device of a main shaft comprises a bearing plate, a bearing seat, an oil storage container, a displacement sensor, a hydrostatic bearing, two constant delivery pumps and two frequency converters; the bearing seat is provided with an inner cavity; the bearing plate is movably arranged in the inner cavity and is fixedly sleeved outside the main shaft; the hydrostatic bearing is sleeved outside the bearing plate in a clearance manner, is positioned in the inner cavity and is arranged on the bearing seat; the hydrostatic bearing has two oil chambers; the two oil cavities are oppositely arranged in the radial direction of the main shaft; the two fixed displacement pumps are arranged in one-to-one correspondence with the two oil cavities and are used for conveying the oil in the oil storage container to the corresponding oil cavities; the two frequency converters are arranged in one-to-one correspondence with the two fixed displacement pumps; the output end of the frequency converter is electrically connected with the input end of the corresponding constant delivery pump, and the input end of the frequency converter is communicated with an external power supply; the displacement sensor is installed on the bearing seat and used for testing the radial displacement of the bearing plate.
Furthermore, the number of the displacement sensors is two, and the two displacement sensors are sequentially arranged along the radial direction of the bearing plate.
Furthermore, the hydrostatic bearing is also provided with an oil return groove and an oil return channel; the notch of the oil return groove faces the bearing plate; the oil return groove is communicated with the oil return groove and the inner cavity; the oil return passage is connected with an oil return pipe, and one end of the oil return pipe, which is far away from the oil return passage, extends into the oil storage container.
Furthermore, the bearing seat is provided with an oil return port communicating the outside with the inner cavity.
Compared with the prior art, the invention has the beneficial effects that:
the bearing plate is fixedly sleeved on the shaft core, the hydrostatic bearing is sleeved outside the bearing plate in a clearance manner, and the rotating speed is respectively adjusted to be n0+nxAnd n0-nxThe two constant delivery pumps respectively correspond to oil cavities of the two hydrostatic bearings for inputting oil, and the oil is sprayed to the bearing plate through the oil cavities of the hydrostatic bearings to realize the alignmentLoading the bearing plate, and enabling the bearing plate to drive the main shaft to rotate; the radial displacement of the main shaft can be obtained by matching with a displacement sensor, so that the dynamic stiffness of the main shaft can be tested; in the whole process, a gap exists between the hydrostatic bearing and the bearing plate, so that safety accidents caused by collision and abrasion can be avoided; moreover, the bearing plate is not in contact with the working state of the hydrostatic bearing, and an oil film formed in the hydrostatic bearing has vibration absorption characteristics, so that vibration is reduced, and the bearing plate has excellent vibration absorption performance.
Drawings
FIG. 1 is a flow chart of a radial dynamic stiffness testing method of a spindle according to the present invention;
FIG. 2 is a schematic structural diagram of a radial dynamic stiffness testing device of a spindle according to the present invention;
fig. 3 is a schematic structural diagram of the radial dynamic stiffness testing device of the main shaft (excluding the oil storage container and the frequency converter).
In the figure: 10. a main shaft; 20. a carrier plate; 30. a bearing seat; 31. an inner cavity; 40. an oil storage container; 50. a displacement sensor; 60. a hydrostatic bearing; 61. an oil chamber; 70. a constant delivery pump; 80. a frequency converter; 90. an oil return groove; 100. an oil return passage; 110. and an oil return port.
Detailed Description
The present invention will be further described with reference to the accompanying drawings and the detailed description, and it should be noted that any combination of the embodiments or technical features described below can be used to form a new embodiment without conflict.
The method for testing the radial dynamic stiffness of the main shaft shown in FIG. 1 comprises the following steps:
the preparation method comprises the following steps: a bearing plate 20 is fixedly sleeved outside the main shaft 10; sleeving a hydrostatic bearing 60 outside the bearing plate 20 in a clearance manner, wherein two oil cavities 61 are formed in the hydrostatic bearing 60; two oil cavities 61 are arranged along the radial direction of the main shaft 10 and are oppositely arranged in the radial direction, so that the loading positions of the two hydrostatic bearings 60 on the bearing plate 20 are the same; the initial gaps between the end surfaces of the two oil cavities 61 where the cavities are located and the bearing plate 20 are the same, namely the gap between the end surface of one oil cavity 61 where the cavity is located and the bearing plate 20 is the same as the gap between the end surface of the other oil cavity 61 where the cavity is located and the bearing plate 20;
and a load applying step: driving the main shaft 10 to rotate; two constant delivery pumps 70 are adopted to correspondingly input oil into the two oil cavities 61 respectively, and at the moment, the constant delivery pumps 70 input external oil into the oil cavities 61 of the hydrostatic bearing 60; then the bearing plate 20 is sprayed from the oil cavity 61 of the hydrostatic bearing 60 to the bearing plate 20, so that the bearing plate 20 is loaded, and the bearing plate 20 is fixed on the main shaft 10, so that the main shaft 10 is loaded; at the same time, the rotation speed V of one of the constant flow pumps 70 is adjusted1Is adjusted to n0+nxAnd the rotational speed V of the other fixed displacement pump 70 is adjusted2Is adjusted to n0-nxBecause the rotating speeds of the two constant delivery pumps 70 are different, namely the oil supply pressures of the two constant delivery pumps 70 are different, the loading force of oil sprayed to the bearing plate 20 is different, and the bearing plate 20 can drive the shaft core to move along the radial direction of the shaft core;
a radial displacement acquisition step: in the step of applying the load, the radial displacement of the bearing plate 20 is tested by using the displacement sensor 50, and as the bearing plate 20 is fixedly connected with the shaft core, the radial displacement x of the main shaft 10 is determined according to the radial displacement of the bearing plate 20;
a calculation step:
calculating the effective bearing area S of the oil chamber 61 according to an area calculation formula; it should be noted that, according to the common knowledge of the skilled person, the area of the oil chamber 61 of the hydrostatic bearing 60 can be calculated by measuring the diameter of the oil chamber 61 of the hydrostatic bearing 60 and then by using an area calculation formula, and details are not described herein;
the oil discharge resistance R of the oil chamber 61 is calculated0；
Calculating the radial dynamic stiffness k of the main shaft 10 according to the formula (1);
wherein, in the above formula (1):
x is the radial displacement of the spindle 10; s is the oil cavity61 effective bearing area; n is0The rated rotation speed of the fixed displacement pump 70; n isxIs the rotational speed V1Or speed of rotation V2A variation amount (absolute value) with respect to the rated rotation speed; q. q.s0The rated oil amount pumped out for each rotation of the constant delivery pump 70; r0The oil outlet resistance of the oil chamber 61; h is0Is the initial gap size;
in the above steps, the hydrostatic bearing 60 and the fixed displacement pump 70 are matched to load the main shaft 10, and a gap exists between the hydrostatic bearing 60 and the bearing plate 20, so that safety accidents caused by collision and abrasion can be avoided; furthermore, the bearing plate 20 is not in contact with the hydrostatic bearing 60 in the operating state, and the oil film formed in the hydrostatic bearing 60 has a vibration absorption characteristic, so that vibration is reduced, and the bearing plate has excellent vibration absorption performance.
It should be noted that the effective bearing area S and the oil discharge resistance R are described above0The calculation formula (b) is common knowledge, and can be known by those skilled in the art according to common knowledge, and will not be described herein again.
Preferably, in the radial displacement obtaining step, two displacement sensors 50 are used to test the radial displacement of the bearing plate 20, and the average value of the values tested by the two displacement sensors 50 is taken as the radial displacement x of the main shaft 10; the accuracy can be improved by obtaining the radial displacement of the spindle 10 from the average of two sensors.
Further, in the step of applying the load, the magnitude of the current supplied to the fixed displacement pump 70 is controlled using the frequency converter 80 to adjust the rotation speed of the fixed displacement pump 70.
Specifically, a flange is employed as the carrier plate 20.
The embodiment also discloses a radial dynamic stiffness testing device of the main shaft as shown in fig. 2-3, which comprises a bearing plate 20, a bearing seat 30, an oil storage container 40, a displacement sensor 50, a hydrostatic bearing 60, two constant displacement pumps 70 and two frequency converters 80; the bearing seat 30 is formed with an inner cavity 31; the bearing plate 20 is movably arranged in the inner cavity 31; the hydrostatic bearing 60 is sleeved outside the bearing plate 20 in a clearance way, is positioned in the inner cavity 31 and is arranged on the bearing seat 30; the hydrostatic bearing 60 has two oil chambers 61; the two oil chambers 61 are arranged oppositely in the radial direction of the main shaft 10; the two fixed displacement pumps 70 are arranged in one-to-one correspondence with the two oil chambers 61, and the fixed displacement pumps 70 are used for conveying the oil in the oil storage container 40 into the corresponding oil chambers 61; the two frequency converters 80 are arranged corresponding to the two constant delivery pumps 70 one by one; the output end of the frequency converter 80 is electrically connected with the input end of the corresponding constant delivery pump 70, and the input end of the frequency converter 80 is communicated with an external power supply; the displacement sensor 50 is mounted on the bearing housing 30 and is used to test the radial displacement of the carrier plate 20.
On the basis of the structure, when the radial dynamic stiffness testing device of the main shaft is used, the main shaft 10 penetrates into the inner cavity 31 and is fixedly arranged in the bearing plate 20 in a penetrating manner; moving the bearing plate 20 to make the size of the gap between the bearing plate 20 and the two oil cavity 61 openings of the hydrostatic bearing 60 consistent; rotating the main shaft 10, controlling the voltage of the power supply of the constant delivery pumps 70 by using the frequency converter 80, and adjusting the rotation speed of one of the constant delivery pumps 70 to n0+nxAnd the rotational speed V of the other fixed displacement pump 70 is adjusted2Is adjusted to n0-nxAt this time, the oil supply pressure of the two fixed displacement pumps 70 is not used, and simultaneously the fixed displacement pumps 70 convey the oil in the oil storage container 40 into the oil cavity 61 of the hydrostatic bearing 60, and the oil is stored in the oil cavity 61 of the hydrostatic bearing 60 and then sprayed to the bearing plate 20, so that the bearing plate 20 is loaded, and the bearing plate 20 is fixedly connected with the main shaft 10, so that the main shaft 10 is loaded; furthermore, the loading force on the opposite sides of the bearing plate 20 is different, so that the bearing plate moves in the radial direction and drives the main shaft 10 to move in the radial direction; at this time, the displacement sensor 50 tests the radial displacement of the bearing plate 20, i.e. obtains the radial displacement of the spindle 10; then, the radial dynamic stiffness k of the main shaft 10 can be calculated according to the formula (1) in a matching manner;
wherein, in the above formula (1):
x is the radial displacement of the spindle 10; s is the effective bearing area; n is0Is the rated rotational speed of the fixed displacement pump 70; n isxIs the rotational speed V1Or speed of rotation V2The variation from the rated speed (the variation isAbsolute value); q. q.s0The rated oil amount pumped out for each rotation of the constant delivery pump 70; r0The oil outlet liquid resistance is obtained; h is0Is the initial gap size.
It should be noted that the oil storage container 40 can be an oil storage tank, an oil storage barrel, an oil storage basin, etc.; the frequency converter 80 is a conventional component, and a method for implementing the power supply voltage control of the constant displacement pump 70 is known in the art, and will not be described herein.
In the process, the hydrostatic bearing 60 is matched with the constant delivery pump 70 to load the main shaft 10, and a gap exists between the hydrostatic bearing 60 and the bearing plate 20, so that safety accidents caused by collision and abrasion can be avoided; furthermore, the bearing plate 20 is not in contact with the hydrostatic bearing 60 in the operating state, and the oil film formed in the hydrostatic bearing 60 has a vibration absorption characteristic, so that vibration is reduced, and the bearing plate has excellent vibration absorption performance.
Further, the number of the displacement sensors 50 is two, the two displacement sensors 50 are sequentially arranged along the radial direction of the bearing plate 20, and then the average value of the values tested by the two displacement sensors 50 is taken as the radial displacement of the main shaft 10, so that the accuracy can be improved.
Specifically, the hydrostatic bearing 60 is further provided with an oil return groove 90 and an oil return passage 100; the notch of the oil return groove 90 faces the bearing plate 20; oil return groove 90 communicates oil return groove 90 with inner cavity 31; the oil return passage 100 is connected with an oil return pipe, and one end of the oil return pipe, which is far away from the oil return passage 100, extends into the oil storage container 40; thus, the oil ejected from the oil chamber 61 of the hydrostatic bearing 60 enters the oil return groove 90 when passing through the position of the oil return groove 90, and then flows into the oil storage container 40 from the oil return passage 100 and the oil return pipe, so that part of the oil is collected and recovered, the oil is prevented from splashing, and the cost is saved.
More specifically, the bearing seat 30 is provided with an oil return opening 110 communicating the outside with the inner cavity 31, so that the oil ejected from the oil cavity 61 of the hydrostatic bearing 60 can flow into the oil storage container 40 from the oil return opening 110 when entering the inner cavity 31 and flowing to the cavity wall of the inner cavity 31, and further collection and recovery of the oil are realized.
The above embodiments are only preferred embodiments of the present invention, and the protection scope of the present invention is not limited thereby, and any insubstantial changes and substitutions made by those skilled in the art based on the present invention are within the protection scope of the present invention.
Claims (8)
1. A radial dynamic stiffness testing method of a main shaft is characterized by comprising the following steps:
the preparation method comprises the following steps: a bearing plate is fixedly sleeved outside the main shaft; sleeving a hydrostatic bearing clearance outside the bearing plate, wherein two oil cavities are formed in the hydrostatic bearing; arranging the two oil cavities along the radial direction of the main shaft and oppositely arranging the two oil cavities in the radial direction; the initial gaps between the end surfaces of the two oil cavities where the cavities are located and the bearing plate are the same in size;
and a load applying step: driving the main shaft to rotate; two constant delivery pumps are adopted to correspondingly input oil into the two oil cavities respectively, and the oil is sprayed to the bearing plate through the oil cavities; at the same time, the rotating speed V of one of the constant delivery pumps is adjusted1Is adjusted to n0+nxAnd the rotational speed V of the other fixed displacement pump is adjusted2Is adjusted to n0-nx；
A radial displacement acquisition step: in the step of applying the load, a displacement sensor is adopted to test the radial displacement of the bearing plate, and the radial displacement x of the main shaft is determined according to the radial displacement of the bearing plate;
a calculation step:
calculating the effective bearing area S of the oil cavity according to an area calculation formula;
calculating the oil discharge resistance R of the oil cavity0；
Calculating the radial dynamic stiffness k of the main shaft according to the formula (1);
wherein, in the above formula (1):
x is the radial displacement of the main shaft(ii) a S is the effective bearing area of the oil cavity; n is0The rated rotating speed of the fixed displacement pump; n isxIs the rotational speed V1Or speed of rotation V2A variation amount with respect to the rated rotation speed; q. q.s0The rated oil quantity pumped out by the fixed displacement pump every time the fixed displacement pump rotates one circle; r0The oil outlet resistance of the oil cavity is set; h is0Is the initial gap size.
2. The radial dynamic stiffness test method of the main shaft according to claim 1, characterized in that: in the radial displacement obtaining step, the two displacement sensors are used for testing the radial displacement of the bearing plate, and the average value of the values tested by the two displacement sensors is taken as the radial displacement x of the main shaft.
3. The radial dynamic stiffness test method of the main shaft according to claim 1, characterized in that: in the step of applying the load, a frequency converter is adopted to control the frequency of a variable frequency motor supplied to the fixed displacement pump so as to adjust the rotating speed of the fixed displacement pump.
4. The radial dynamic stiffness test method of the main shaft according to claim 1, characterized in that: a flange is used as the carrier plate.
5. The utility model provides a radial dynamic stiffness testing arrangement of main shaft which characterized in that: the device comprises a bearing plate, a bearing seat, an oil storage container, a displacement sensor, a hydrostatic bearing, two constant delivery pumps and two frequency converters; the bearing seat is provided with an inner cavity; the bearing plate is movably arranged in the inner cavity and is fixedly sleeved outside the main shaft; the hydrostatic bearing is sleeved outside the bearing plate in a clearance manner, is positioned in the inner cavity and is arranged on the bearing seat; the hydrostatic bearing has two oil chambers; the two oil cavities are oppositely arranged in the radial direction of the main shaft; the two fixed displacement pumps are arranged in one-to-one correspondence with the two oil cavities and are used for conveying the oil in the oil storage container to the corresponding oil cavities; the two frequency converters are arranged in one-to-one correspondence with the two fixed displacement pumps; the output end of the frequency converter is electrically connected with the input end of the corresponding constant delivery pump, and the input end of the frequency converter is communicated with an external power supply; the displacement sensor is installed on the bearing seat and used for testing the radial displacement of the bearing plate.
6. The radial dynamic stiffness test device of a spindle according to claim 5, wherein: the number of the displacement sensors is two, and the two displacement sensors are sequentially arranged along the radial direction of the bearing plate.
7. The radial dynamic stiffness test device of a spindle according to claim 5, wherein: the hydrostatic bearing is also provided with an oil return groove and an oil return channel; the notch of the oil return groove faces the bearing plate; the oil return groove is communicated with the oil return groove and the inner cavity; the oil return passage is connected with an oil return pipe, and one end of the oil return pipe, which is far away from the oil return passage, extends into the oil storage container.
8. The radial dynamic stiffness test device of a spindle according to claim 5, wherein: the bearing seat is provided with an oil return port communicated with the outside and the inner cavity.
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| CN201811556862.7A CN109765015B (en) | 2018-12-19 | 2018-12-19 | Method and device for testing radial dynamic stiffness of main shaft |
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| CN201811556862.7A CN109765015B (en) | 2018-12-19 | 2018-12-19 | Method and device for testing radial dynamic stiffness of main shaft |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101718658B (en) * | 2009-11-17 | 2011-11-09 | 重庆大学 | Device for testing dynamic stiffness and constant pressure of high-speed electric spindle |
| KR101103469B1 (en) * | 2010-03-31 | 2012-01-09 | 창원대학교 산학협력단 | Measuring apparatus for dynamic stiffness |
| CN102032988B (en) * | 2010-11-26 | 2012-07-04 | 西安交通大学 | Decoupling measurement method for dynamic rigidity of hydrodynamic thrust bearing |
| CN102980755B (en) * | 2012-11-16 | 2015-05-20 | 北京工业大学 | Quantitive type experimental device for dynamic and static performances of static-pressure rotary table |
| CN203053702U (en) * | 2013-01-05 | 2013-07-10 | 西安交通大学 | Dynamic and static stiffness testing device for angular contact ball bearing |
| CN205719522U (en) * | 2016-06-13 | 2016-11-23 | 天津迈博机械设备有限公司 | A kind of electro spindle Static stiffness test device |
| CN106885663B (en) * | 2017-02-21 | 2019-11-08 | 清华大学深圳研究生院 | A kind of machine tool chief axis stiffness test method and its system |
| CN108414169B (en) * | 2018-03-08 | 2019-07-09 | 湖南大学 | A kind of high speed rotation shafting dynamic axial load stiffness test method and device |
| CN108414202B (en) * | 2018-03-08 | 2019-07-09 | 湖南大学 | A kind of high speed rotation shafting dynamic radial load stiffness test method and device |
| CN108692896B (en) * | 2018-05-07 | 2019-05-07 | 北京科技大学 | A kind of non-contact air film loading device suitable for high-speed main spindle rigidity test |
| CN108680357A (en) * | 2018-06-25 | 2018-10-19 | 南京航空航天大学 | A kind of axial and radial comprehensive dynamic stiffness measurement device of rolling bearing |
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