CN109145406A - Method for determining critical dimension of bearing simulator - Google Patents
Method for determining critical dimension of bearing simulator Download PDFInfo
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- CN109145406A CN109145406A CN201810862830.3A CN201810862830A CN109145406A CN 109145406 A CN109145406 A CN 109145406A CN 201810862830 A CN201810862830 A CN 201810862830A CN 109145406 A CN109145406 A CN 109145406A
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- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- G—PHYSICS
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Abstract
The invention discloses a method for determining the key size of a bearing simulator, which determines the data information of the bearing simulator according to the relation between the characteristic parameters of a simulation test device and the characteristic parameters of a simulated object rolling bearing and a simulated object, and determines the diameter d of the bearing simulator according to the data information of the simulated object rolling bearings1Inner diameter d of scale rings2And the major diameter d of the cylindrical bosss3And its distribution circle diameter ds4. Based on the similarity theory in fluid mechanics, the structure and the size calculation proportion of the bearing simulator are determined, the flow similarity can be ensured, and the flow state of lubricating oil in the bearing simulator can be ensured to effectively simulate the process of the movement and the development of the lubricating oil on the surface of a rotating part of a rolling bearing.
Description
Technical field
The invention belongs to high speed roller bearing the field of test technology, and in particular to a kind of critical size of Bearing SIMULATOR is true
Determine method.
Background technique
The high speed roller bearing of high speed roller bearing, especially aircraft power plant generallys use fuel feeding under oil spout or ring
Lubrication, lubricating oil forms lubricating oil film on the rotating motion parts such as bearing inner race, retainer and rolling element surface, in high speed rotor
Under the action of oil film along movement parts apparent motion, and it is separated at the edge on these surfaces, be broken for oily band and oil droplet, oily band
The bearing that is connected with high speed roller bearing is got rid of with oil droplet to receive in oil and oil return apparatus, this process realize bearing lubrication and
It is cooling.The state development of high speed roller bearing rotating motion part sea surface oil slick will have a direct impact on the lubrication and cooling function of bearing
Can, and have a significant impact to the efficiency of lubricating oil oil-collecting device thereafter.It is directly logical since aircraft power plant structure is extremely complex
Physics bench test is crossed effectively to measure the state development relevant parameter of high speed roller bearing rotating motion part sea surface oil slick
It is extremely difficult, and take time and effort enterprise at high cost.
Summary of the invention
In view of this, the main purpose of the present invention is to provide a kind of critical sizes of Bearing SIMULATOR to determine method.
In order to achieve the above objectives, the technical scheme of the present invention is realized as follows:
The critical size that the embodiment of the present invention provides a kind of Bearing SIMULATOR determines method, this method are as follows: is tried according to simulation
The characteristic parameter of experiment device and the characteristic parameter relationship of institute's simulated object rolling bearing and simulated object determine Bearing SIMULATOR
Data information, the diameter d of Bearing SIMULATOR is determined according to the data information of the simulated object rolling bearings1, in calibration loop
Diameter ds2, cylinder boss major diameter ds3With its pitch circle diameter ds4。
In above scheme, the characteristic parameter of the simulation test device and the characteristic parameter of institute's simulated object rolling bearing are closed
System isρbTo lubricate oil density, n in institute's simulated object rolling bearingbFor institute's simulated object axis of rolling
The limit speed held, dbFor the characteristic size of institute's simulated object rolling bearing, σbTo lubricate oil meter in institute's simulated object rolling bearing
Face tension, ρsTo lubricate oil density, n in simulation test devicesFor the limit speed of simulation test device shaft, dbFor simulation examination
The characteristic size of experiment device, σsFor lubricant oil surface tension in simulation test device.
In above scheme, the data information according to the simulated object rolling bearing determines the diameter of Bearing SIMULATOR
ds1, calibration loop internal diameter ds2, cylinder boss major diameter ds3With its pitch circle diameter ds4, specifically: according to formula ds1=kdb1、ds2=
kdb2、ds3=kdb3、ds4=kdb4The diameter d of Bearing SIMULATOR is determined respectivelys1, calibration loop internal diameter ds2, cylinder boss major diameter ds3
With its pitch circle diameter ds4；Wherein, k is the critical size conversion scale of simulation test device and simulated object rolling bearing.
In above scheme, the critical size conversion scale k of the simulation test device and simulated object rolling bearing passes throughIt determines.
Compared with prior art, beneficial effects of the present invention:
The present invention is based on the theories of similarity in hydrodynamics, determine the structure and size calculating ratio of its Bearing SIMULATOR
Example, can guarantee to flow similar, can guarantee that the flow regime of lubricating oil in Bearing SIMULATOR can effectively simulate lubricating oil and exist
The process of rolling bearing revolving part apparent motion and development.
Detailed description of the invention
Fig. 1 is the structural schematic diagram for the experimental rig that the present invention applies；
Fig. 2 is speed change system schematic diagram；
Fig. 3 is lifting platform structural schematic diagram；
Fig. 4 is bearing part schematic diagram；
Fig. 5 is abutment sleeve structural schematic diagram；
Fig. 6 is shaft sleeve structural schematic diagram；
Fig. 7 is small pulley structural schematic diagram；
Fig. 8 is capsule components schematic diagram；
Fig. 9 is right end cover plate center attachment structure schematic diagram；
Figure 10 is Bearing SIMULATOR structural schematic diagram；
Figure 11 is calibration loop structural schematic diagram；
Figure 12 is cylinder boss structural schematic diagram；
Figure 13 is fuel feeding oil return and lubricating system schematic diagram；
Specific embodiment
In order to make the objectives, technical solutions, and advantages of the present invention clearer, with reference to the accompanying drawings and embodiments, right
The present invention is further elaborated.It should be appreciated that the specific embodiments described herein are merely illustrative of the present invention, and
It is not used in the restriction present invention.
The critical size that the embodiment of the present invention provides a kind of Bearing SIMULATOR determines method, this method are as follows: is tried according to simulation
The characteristic parameter of experiment device and the characteristic parameter relationship of institute's simulated object rolling bearing and simulated object determine that simulated object is rolled
The data information of dynamic bearing determines the diameter d of Bearing SIMULATOR according to the data information of the simulated object rolling bearings1, carve
Spend ring internal diameter ds2, cylinder boss major diameter ds3With its pitch circle diameter ds4。
The characteristic parameter of the simulation test device and the characteristic parameter relationship of institute's simulated object rolling bearing areρbTo lubricate oil density, n in institute's simulated object rolling bearingbFor institute's simulated object rolling bearing
Limit speed, dbFor the characteristic size of institute's simulated object rolling bearing, σbFor lubricant oil surface in institute's simulated object rolling bearing
Power, ρsTo lubricate oil density, n in simulation test devicesFor the limit speed of simulation test device shaft, dbFor simulation test dress
The characteristic size set, σsFor lubricant oil surface tension in simulation test device.
The data information according to the simulated object rolling bearing determines the diameter d of Bearing SIMULATORs1, in calibration loop
Diameter ds2, cylinder boss major diameter ds3With its pitch circle diameter ds4, specifically: according to formula ds1=kdb1、ds2=kdb2、ds3=
kdb3、ds4=kdb4The diameter d of Bearing SIMULATOR is determined respectivelys1, calibration loop internal diameter ds2, cylinder boss major diameter ds3With its distribution circle
Diameter ds4；Wherein, k is the critical size conversion scale of simulation test device and simulated object rolling bearing.
The critical size conversion scale k of the simulation test device and simulated object rolling bearing passes throughIt determines.
Embodiment:
The critical size that Bearing SIMULATOR is carried out using angular contact ball bearing 7008AC as simulated object determines method.
Step 1: using angular contact ball bearing 7008AC as simulated object, determine in institute's simulated object rolling bearing lubricating oil with
Lubricating oil physical property is identical in simulation test device, i.e. ρb=ρs, σs=σs.Determine institute simulated object angular contact ball bearing 7008AC
In oil lubrication, its limit speed is nbFor 11000r/min, the outer ring angular contact ball bearing 7008AC outside diameter db1For 68mm,
Outer ring internal diameter db2For 60mm, rolling bearing rolling element diameter db3For 8mm, rolling bearing rolling element pitch circle diameter db4For 54mm,
Determine that motor limit speed is n in this experimental rigeFor 2890r/min, V belt translation transmission ratio, that is, small pulley and big belt wheel are calculated
It is 1:4 that diameter ratio, which is i,；Then the limit speed of shaft is nsFor ne/i；
Step 2: calculating the critical size conversion scale k of Bearing SIMULATOR and simulated object rolling bearing, such as using formula
Under:
Step 3: calculating Bearing SIMULATOR diameter ds1, calibration loop internal diameter ds2, cylinder boss major diameter ds3With its pitch circle diameter
ds4, as follows using formula
ds1=kdb1=0.9674 × 68=65.78
ds2=kdb2=0.9674 × 60=58.04
ds3=kdb3=0.9674 × 8=7.74
ds4=kdb4=0.9674 × 54=52.24.
The present invention is applied to the experimental rig of simulation high speed roller bearing rotating motion part sea surface oil slick state development, such as schemes
Shown in 1, including speed change system 1, mechanical structure ontology 2 and fuel feeding oil return and lubricating system 3；The mechanical structure ontology 2 wraps
Include lifting platform, bearing part and capsule components.
The speed change system 1 is used to provide power for shaft 23 and adjust the revolving speed of shaft.As shown in Fig. 2, in power electric
It is sequentially ingressed into breaker 6, contactor 7, filter 8 on source 5, provides stable, interference-free AC power source for frequency converter 9,
And control the start and stop of frequency converter 9.Frequency converter 9 is connected with 10 input terminal of motor, in the output end and belt driver of motor 10
Big belt wheel 11 is connected, and motor 10 drives big belt wheel 11 to rotate, and big belt wheel 11 drives small pulley 22 to rotate by transmission belt 12.Revolving speed
Measuring system 4 measures the revolving speed of shaft, and speed measuring system 4 uses laser tachometer.According to desired speed and laser tachometer
The working frequency of the difference between actual speed measured, fine tuning frequency converter 9 makes shaft 23 reach stable desired speed.
As shown in figure 3, lifting platform includes pedestal 13, handle 14, threaded rod 15, support base 16, sliding block 17 and guide post 18.Branch
Support seat 16 is fixedly connected by bolt with pedestal 13, and guide post 18 and threaded rod 15 connect with support base 16 respectively and across supporting
Seat 16, guide post 18 pass through 17 inner hole of sliding block, and 17 threaded hole of sliding block and threaded rod 15 cooperate, and handle 14 passes through screw thread and threaded rod 15
It is fixedly connected, and rotational handle 14 can drive threaded rod 15 to rotate and then sliding block 17 is driven to move.
As shown in figure 4, bearing part includes bracket 19, bearing block 20, bearing (ball) cover 21, small pulley 22, shaft 23, oil pipe
Connector 24, nipple 25, round nut 26, temperature-sensing probe 27, abutment sleeve 28, shaft sleeve 29 and rolling bearing 30.Sliding block 17
Upper surface is fixed by bolt and bracket 19, and 19 upper surface of bracket is bolted to connection with bearing block 20；Bearing block 20 is
The outer ring of rolling bearing 30 and the tooth pad of shaft 23 are the hollow cylindrical structure with end flanges, end face method
Blue circumferential direction is provided with several mounting-positioning holes being evenly arranged, and the inner hole of the reference circle and bearing block 20 of mounting-positioning holes is same
The heart has 8 mounting-positioning holes in the present embodiment, offers the threaded hole connecting with nipple 25 above bearing block 20, is axis
27 offer lubricating oil are provided；Shaft 23 is the cylindrical parts that one end has ring flange, and the circumferential direction of ring flange is provided with several uniform
The mounting-positioning holes of arrangement, the reference circle and shaft 23 of mounting-positioning holes are concentric, there is 6 mounting-positioning holes in the present embodiment, turn
Axis 18 passes through bearing block 20 and by the outer ring of rolling bearing 30 and the cylinder of bearing block 20 of installation on its outer surface
Surface engagement, the left end of shaft 23 are fixedly connected with the small pulley 22 of V belt translation, and right end protrudes into cavity；The inner ring of rolling bearing 30
The shaft sleeve 29 between bearing is set with merga pass with 23 outer surface of shaft and carries out axially position；The inner surface of shaft sleeve 29 with
The cooperation of 23 outer surface of shaft；The outer ring outer surface of rolling bearing 30 and the hollow cylinder inner surface of bearing block 20 match merga pass
The abutment sleeve 28 being arranged between bearing carries out axially position, the outer surface of abutment sleeve 28 and the hollow cylinder of bearing block 20
Inner surface cooperation；Round nut 26 is arranged at the rolling bearing 30 of left end, is fixedly connected by screw thread with shaft 23, limits left end
The axial position of rolling bearing 30；Bearing (ball) cover 21 is the flanged type structure for being provided with centre bore, and it is close that annular is offered on centre bore
Sealing groove, bearing (ball) cover 21 pass through shaft 23 and are fixedly connected by bolt with the left side of bearing block 20, be provided in seal groove close
Seal prevents lubricating oil from leaking from 20 left end of bearing block, is provided with threaded hole, nipple 25 and bearing end on bearing (ball) cover 21
Lid 21 is connected through a screw thread；Small pulley 22 is fixedly connected by retaining ring, bolt and flat key with shaft 23；Nipple 25 passes through spiral shell
Line is connect with the threaded hole of bearing (ball) cover 21 and bearing block 20 respectively guarantees flowing in and out for lubricating oil；Oil connection 24 passes through
Screw thread is connect with nipple 25.
As shown in figure 5, abutment sleeve 28 is hollow cylinder part, it is axially provided with the through-hole across barrel.
As shown in fig. 6, shaft sleeve 29 is hollow cylinder part, external cylindrical surface is circumferentially provided with helical opening channel,
Shaft sleeve 29 is rotated synchronously with shaft 23, drive the lubricating oil rotational flow that flows into from the threaded hole of bearing block 20 and make its along
Helical duct flows to the rolling bearing 30 at both ends respectively, provides the lubricating oil of lubrication and cooling for rolling bearing 30.
As shown in fig. 7, small pulley 22 is the belt wheel for having two-stage difference wheel footpath, path wheel surface is provided with circumferential be uniformly distributed
Round bottom shallow grooves, have flat rubber belting wheel rim surface characteristics, 11 collective effect of big belt wheel with 10 output end of motor is to improve shaft
23 revolving speed；Major diameter wheel surface is provided with V-groove, has V-type belt wheel edge surface characteristics, the big belt wheel 11 with 10 output end of motor
Collective effect is to keep or reduce the revolving speed of shaft 23；Shaft 23 can be realized in the case where being changed without 23 upper belt-wheel of shaft
Speedup and deceleration provide bigger range of speeds section for shaft 23；The circumferential direction of 22 path wheel surface of small pulley setting
Equally distributed round bottom shallow grooves can prevent from being driven due to wheel rim surface forms air cushion with transmission interband when high-speed rotation
The phenomenon that band skids.
As shown in figure 8, capsule components include oil connection 24, nipple 25, left end cover 31, cylinder 38, bearing mould
Quasi- device 32, calibration loop 33, cylinder boss 34, right end cover plate 35, the convex disk 36 of connection and jet pipe 37.
Specifically, left end cover 31 is the annular element for being provided with central through hole, outer rim and central hole are provided with positioning
The inner cylinder face left end of ring-shaped step, outer rim positioning ring-shaped step insertion cylinder 38 cooperates with it, carries out tightening by bolt
Connection, and it is overlapped its axis；The end flanges positioning of the centre bore positioning ring-shaped step insertion bearing block 20 of left end cover 31
Cylindrical surface cooperates with it, and is fixedly connected by bolt with bearing block 20, and left end cover 31 is overlapped with the axis of bearing block 20；Turn
Cylinder 38 is protruded at the ring flange end of axis 23, and cooperates with the left side of Bearing SIMULATOR 32, is fixedly connected by screw, shaft and
The axis of Bearing SIMULATOR 32 is overlapped；Cylinder 38 is the transparent cylinder shape component for being provided with exhaust outlet and oil discharge outlet, exhaust outlet and
Oil discharge outlet is arranged symmetrically, and exhaust outlet is communicated with atmosphere, and oil discharge outlet connects with the nipple of oil return line, passes back into lubricating oil
Fuel tank, in the present embodiment, cylinder 38 is made of organic glass；Right end cover plate 35 is the transparent disc shape component of center aperture,
Two sides are provided centrally with a pair of of groove type step, and outer rim is provided with positioning ring-shaped step, and outer rim positions ring-shaped step insertion
Inner cylinder face right end and its of cylinder 38 cooperate, by bolt tightening connection, left end cover 31, cylinder 38 and right end cover plate 35
Axis is overlapped, and in the present embodiment, right end cover plate 35 is made of organic glass.
As shown in figure 9,35 two sides of right end cover plate are provided centrally with groove type step, the left and right end face of right end cover plate 35 is equal
The one convex disk 36 of connection of setting, connecting convex disk 36 is the annulus part component for being provided with central boss and center thread through hole, center
The outer surface of boss and the inner surface of 35 center groove step of right end cover plate cooperate, and connect by the way that bolt and right end cover plate 35 are fixed
It connects, the gap connected between convex disk 36 and right end cover plate 35 is sealed by sealing ring, to prevent oil leak；Nipple 25
External screw thread be screwed into its screwed hole of centre from the left and right side end face for connecting convex disk 36 respectively, carry out tightening connection, oil connection 24
With the internal screw thread tightening connection of right end nipple 25；Jet pipe 37 is that one end has externally threaded hollow circular-tube, the end of thread and a left side
The internal screw thread connection for holding nipple 25, is threaded into the fuel-displaced of the length adjustment jet pipe 37 of connector by adjusting spout threads end
The relative position at end and Bearing SIMULATOR 32, the axis of jet pipe 37 and the axis of Bearing SIMULATOR 32 are overlapped, and flow through jet pipe 37
Lubricating oil is ejected into the center of Bearing SIMULATOR 32, and in the present embodiment, the internal diameter of jet pipe 37 is 6mm, outer diameter 10mm.
As shown in Figure 10, Bearing SIMULATOR 32 is flanged (FLGD) shallow flat concave shaped disk of edge, flat bottom surface and end face
Circumferentially it is uniformly arranged threaded hole；
As shown in figure 11, calibration loop 33 is that end face is provided with the ring-shape accessory of circumferential graduated scale, diameter of bore by
The high speed roller bearing size of simulation determines, the range and precision of graduated scale are according to the geometric dimension and measurement accuracy meter of bearing
It calculates and determines, calibration loop 33 is fixedly and coaxially connected by screw with Bearing SIMULATOR 32, and calibration loop can be in order in the related examination of progress
It tests middle oil band number and oil droplet correlation properties measures.
As shown in figure 12, cylinder boss path is provided with screw thread, and cylinder boss and Bearing SIMULATOR are threadably secured company
It connects.The number of cylinder boss and setting position are passed through by rolling element number, the size and location parameter of the high speed roller bearing simulated
It calculates and determines, in the present embodiment, it is convex that the shallow edge flat concave shaped disk end of Bearing SIMULATOR 32 is circumferentially provided with 12 small columns
Platform can effectively simulate effect of the rolling element for lubricating oil of rolling bearing.
As shown in figure 13, fuel feeding oil return and lubricating system are that jet pipe 37 provides temperature and the adjustable lubricating oil of flow, and is
Bearing block 20 provides quantitative oil lubrication rolling bearing 30, is collected simultaneously from the oil discharge outlet of bearing (ball) cover 21 and cylinder 38 and returns
The lubricating oil of stream.Fuel tank 52 stores lubricating oil, and Oil pump electrical machinery 42 drives oil pump 41 by the lubricating oil in fuel tank 52 through oil filter 40
It is pumped into oil feed line, oil feed line is divided into three fuel feeding, lubrication and overflow branches, and fuel feeding branch is sequentially connected throttle valve 43 and stream
The fuel feeding branch between throttle valve 43 and oil pump 41 is arranged in meter 44, pressure gauge 46, and pressure gauge 46 connects in pressure meter switch 45
Outlet end, and its input end connects with pipeline, oil connection 24 connect in the end of fuel feeding branch, and are connected to right end cover plate 35
Nipple 25 connects；Lubrication branch is connected with electric temperature control valve 47, and branch end connects oil connection 24, oil connection 24 and axis
The nipple 25 connected on seat 20 is held to be connected；Temperature-sensing probe 27 is mounted at rolling bearing 30, and temperature-sensing probe 27 is by bearing block
For temperature feedback inside 20 to electric temperature control valve 47, axis is may be implemented in the control lubrication branch flow of lubrication of electric temperature control valve 47
It holds rolling bearing 30 in seat 20 and lubricates better lubrication.Overflow valve 48, branch end and fuel tank 52 are set in overflow branch
Connection, the fuel feeding lubricating oil extra with lubrication branch pass back into fuel tank by overflow branch；Oil return branch one end respectively with bearing
End cap 21 is connected with the oil discharge outlet of cylinder 38, and the other end accesses fuel tank 52, is arranged in 40 filtering lubricant oil of oil filter in pipeline
Impurity；Liquidometer 39 and thermometer 49 are set on fuel tank 52, and liquidometer 39 monitors lubricating oil liquid level position in fuel tank 52, that is, monitors
Lubricants capacity, thermometer 49 monitor the temperature of lubricating oil in fuel tank；Temperature-sensing probe 27 and heating tube 51 are mounted on 52 bottom of fuel tank,
By the temperature feedback of lubricating oil to temperature controller 50, temperature controller 50 controls heating tube 51 and heats lubricating oil, Ke Yishi temperature-sensing probe 27
Lubricating oil temperature is more accurately controlled in existing fuel tank.
When the present embodiment carries out correlation test research, external impetus power supply 5 is connected, power is arranged according to desired speed and is adjusted
The working frequency of frequency converter 9 in speed system, starts laser tachometer 4 after the stabilization of speed of shaft 23, and measurement shaft 23 turns
Speed, according to the difference of desired speed and actual speed, the working frequency for finely tuning frequency converter 9 makes shaft 23 reach stable predetermined turn
Speed, and record the tachometer value；Then according to scheduled lubricating oil temperature, the computer heating control temperature of temperature controller 50, heating tube are set
Lubricating oil in fuel tank 52 is heated to predetermined temperature according to the control signal of temperature-sensing probe 27 and temperature controller 50 and kept constant by 51
Oil temperature, heating tube 51 stop working, and when lubricating oil temperature loses more than 1 DEG C, heating system will start automatically carries out lubricating oil
Heating and heat preservation, record lubricating oil temperature angle value；According to the flow feedback of flowmeter 44, joint adjusts fuel feeding oil return and lubricating system
The aperture of the overflow valve 48 in throttle valve 43 and overflow branch in middle fuel feeding and lubrication branch, makes the lubrication of fuel feeding branch
Oil stream amount and temperature stabilization and the lubricants capacity for reaching test requirements document, while lubricating branch feed back to electronic according to temperature-sensing probe 27
Its uninterrupted of 47 Signal Regulation of thermostat valve guarantee 30 lubrication needs of rolling bearing, and record fuel feeding branch flow of lubrication and
Temperature.
The foregoing is only a preferred embodiment of the present invention, is not intended to limit the scope of the present invention.
Claims (4)
1. a kind of critical size of Bearing SIMULATOR determines method, which is characterized in that this method are as follows: according to simulation test device
The characteristic parameter relationship and simulated object of characteristic parameter and institute's simulated object rolling bearing determine that the data of Bearing SIMULATOR are believed
Breath, the diameter d of Bearing SIMULATOR is determined according to the data information of the simulated object rolling bearings1, calibration loop internal diameter ds2, circle
Column boss major diameter ds3With its pitch circle diameter ds4。
2. a kind of critical size of Bearing SIMULATOR according to claim 1 determines method, which is characterized in that the simulation
The characteristic parameter of experimental rig and the characteristic parameter relationship of institute's simulated object rolling bearing areρbFor institute
Oil density, n are lubricated in simulated object rolling bearingbFor the limit speed of institute's simulated object rolling bearing, dbFor the rolling of institute's simulated object
The characteristic size of dynamic bearing, σbFor lubricant oil surface tension in institute's simulated object rolling bearing, ρsTo be lubricated in simulation test device
Oil density, nsFor the limit speed of simulation test device shaft, dbFor the characteristic size of simulation test device, σsFor simulation test
Lubricant oil surface tension in device.
3. a kind of critical size of Bearing SIMULATOR according to claim 1 or 2 determines method, which is characterized in that described
The diameter d of Bearing SIMULATOR is determined according to the data information of the simulated object rolling bearings1, calibration loop internal diameter ds2, cylinder it is convex
Platform major diameter ds3With its pitch circle diameter ds4, specifically: according to formula ds1=kdb1、ds2=kdb2、ds3=kdb3、ds4=kdb4Point
Not Que Ding Bearing SIMULATOR diameter ds1, calibration loop internal diameter ds2, cylinder boss major diameter ds3With its pitch circle diameter ds4；Wherein, k
For the critical size conversion scale of simulation test device and simulated object rolling bearing.
4. a kind of critical size of Bearing SIMULATOR according to claim 3 determines method, which is characterized in that the simulation
The critical size conversion scale k of experimental rig and simulated object rolling bearing passes throughIt determines.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810862830.3A CN109145406B (en) | 2018-08-01 | 2018-08-01 | Method for determining critical dimension of bearing simulator |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201810862830.3A CN109145406B (en) | 2018-08-01 | 2018-08-01 | Method for determining critical dimension of bearing simulator |
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| CN109145406B CN109145406B (en) | 2022-05-13 |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4445365A (en) * | 1982-05-17 | 1984-05-01 | Selby Theodore W | Tapered bearing simulator-viscometer |
| CN2030930U (en) * | 1988-03-17 | 1989-01-18 | 浙江大学 | Thermal insulating cooling sleeve for precision spindle system |
| CN105547663A (en) * | 2015-12-04 | 2016-05-04 | 中国南方航空工业(集团)有限公司 | Bearing simulator flow direction test clamp |
-
2018
- 2018-08-01 CN CN201810862830.3A patent/CN109145406B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4445365A (en) * | 1982-05-17 | 1984-05-01 | Selby Theodore W | Tapered bearing simulator-viscometer |
| CN2030930U (en) * | 1988-03-17 | 1989-01-18 | 浙江大学 | Thermal insulating cooling sleeve for precision spindle system |
| CN105547663A (en) * | 2015-12-04 | 2016-05-04 | 中国南方航空工业(集团)有限公司 | Bearing simulator flow direction test clamp |
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| Title |
|---|
| WANG YAN等: "Automatic mass balancing and design of a six degrees-of-freedom air bearing spacecraft simulator", 《IEEE》 * |
| 史宝军等: "磁头/磁盘间分子力对超低飞行高度浮动块动力学性能的影响", 《兵工学报 》 * |
| 陈薄等: "轴承腔气相介质流场的理论与试验", 《航空动力学报》 * |
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