CN103528945A - Friction measurement device - Google Patents
Friction measurement device Download PDFInfo
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- CN103528945A CN103528945A CN201310449208.7A CN201310449208A CN103528945A CN 103528945 A CN103528945 A CN 103528945A CN 201310449208 A CN201310449208 A CN 201310449208A CN 103528945 A CN103528945 A CN 103528945A
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Abstract
The invention relates to a friction measurement device which comprises a disk drive system, a ball drive system, a displacement adjusting system, an angle adjusting system, a loading system, a lubricating system and a test system, wherein the disk drive system drives a disc to rotate through a disc shaft; the ball drive system drives a ball to rotate through a ball shaft; the displacement adjusting system is used for adjusting the relative position between the disc and the ball; the angle adjusting system is used for adjusting the angle between the disc shaft and the ball shaft; the loading system is used for providing a loading force for the disc and the ball; the lubricating system is used for providing lubricating oil for the disc and the ball; and the test system is used for measuring the friction force between the disc and the ball through a tension sensor. The friction measurement device not only can test the friction lubricating property under a high-speed medium-loading working condition but also has the characteristics of high measurement accuracy, good stability and the like.
Description
Technical field
The present invention relates to a kind of rub measurement device, relate in particular to the rub measurement device under a kind of high-speed condition.
Background technology
Along with the demand of space flight, aviation, navigation, the industry development of high ferro equipment, equipment is manufactured to high precision, high-speed, high-level efficiency future development, and corresponding equipment need to move under the harsh conditions such as high speed, high temperature.High-speed railway vehicle main shaft bearing linear velocity is about 40m/s; Aero-engine Bearing maximum line velocity is about 180m/s; Electricity maximum speed of spindle can reach 200,000 revs/min, and superhigh speed grinding can reach 300m/s.Lubrication friction state at a high speed, under Super High Speed Condition, to improving bearing life, improves working (machining) efficiency and stability most important.
At a high speed lower huge centrifugal force and thermal effect cause that to contact dynamic loading large, and contact stress is large, temperature rise.Directly have influence on contact region pressure distribution and Temperature Distribution, cause lubricating oil property and rheological properties to change, lubricating oil be no longer shearing force with the simple Newtonian fluid of shear strain linear change, and show complicated non-Newtonianism, thus the film forming of having influence on and carrying.Lubricant deterioration even can occur when temperature rise is too high and lost efficacy, friction pair directly contacts and the inefficacy of adhering.At a high speed the design of equipment is in the urgent need to providing the important parameters such as friction force, friction factor, thickness, lubricant of the friction pairs such as bearing of this equipment.
Up to now, in domestic and foreign literature data, still can not discover and seize the significant data parameters such as the friction force of equipping friction pair under high-speed cruising condition, friction factor, lubricant; Domestic and international existing friction performance testing instrument, comprises the testing tool of also not finding to obtain above-mentioned data parameters in technological invention patent, and therefore, under development high speed, Super High Speed Condition, the testing tool of friction, lubrication performance is very necessary.
In addition, friction testing device of the prior art and measuring method, the existence due to himself some Systematic Errors and original reason error, causes the precision of its measurement lower, and therefore the application in some precision measurements is also restricted.
Summary of the invention
In view of this, necessaryly provide a kind of rub measurement device, this rub measurement device not only can be tested and in (being more than or equal to 100m/s), carry the friction, lubrication performance under operating mode at a high speed, and has the features such as measuring accuracy is high, good stability.
A device, it comprises: a disc driving system, drives a disc spins by a dish axle; One ball drive system, drives a ball to rotate by a ball journal; One displacement regulating system, for regulating the relative position between described dish and ball; One angular adjustment system, for regulating the angle between described dish axle and ball journal; One loading system, for providing loading force between described dish and ball; One lubricating system, for providing lubricating oil between described dish and ball; And a test macro, by a tension-compression sensor, measure the friction force between described dish and ball.
Described disc driving system further comprises a dish electricity main shaft, between described dish electricity main shaft, dish axle and dish, is all fixedly connected with; Described ball drive system further comprises a ball electricity main shaft, between described ball electricity main shaft, ball journal and ball, is all fixedly connected with.
Described displacement regulating system comprises a lifting table and a horizontal guide rail; Described lifting table is for regulating the upper and lower displacement of described dish, and described horizontal guide rail is fixedly installed on the table top of described lifting table, for regulating the horizontal shift of described dish.Described angular adjustment system comprises a worm screw and a friction pulley; Described worm screw is for regulating the anglec of rotation of described ball, and described friction pulley is for the position of fixing described ball.
Described loading system comprises a loading spring and a force cell; Described loading spring slides and is arranged on described horizontal guide rail, for provide loading force between described dish and ball; Described force cell and described loading spring are oppositely arranged and are fixedly installed on described disc driving system, the loading force providing for measuring described loading spring; The direction of described loading force is consistent with the bearing of trend of described horizontal guide rail, vertical with the direction of described friction force.
Described test macro further comprises an air-float guide rail, at least one air-float guide rail slide block and at least one fixture block support; Described air-float guide rail slide block slides and is arranged on described air-float guide rail; Described fixture block bracket holder is located on described air-float guide rail; Described tension-compression sensor is fixedly connected on described fixture block support, and for measuring the pressure in the horizontal direction acting on this tension-compression sensor, the direction of described pressure is consistent with the direction of described friction force or contrary.
Compared with prior art, rub measurement device provided by the invention, can be at contact hertz stress 1GPa, and Entrainment Velocity surpasses the friction force of measuring friction pair in described device under 100m/s condition; Can be by adjusting relative position between described dish and the ball original reason error when reducing friction measurement; The systematic error when mode that can be fixedly connected with described ball, dish by described electric main shaft and the mode that adopts air-float guide rail reduce friction measurement.Rub measurement device provided by the invention, can evaluate lubricant at lubricating property and friction and wear behavior at a high speed and under the harsh conditions of high temperature, for the design of the friction pairs such as bearing equipped at a high speed provides friction, lubrication parameter and technical basis.
Accompanying drawing explanation
The front elevation of the rub measurement device that Fig. 1 provides for the embodiment of the present invention.
The side view of the rub measurement device that Fig. 2 provides for the embodiment of the present invention.
The angle schematic diagram of the ball journal in the rub measurement device that Fig. 3 provides for the embodiment of the present invention and dish axle.
Main element symbol description
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1 |
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10 |
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30 |
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40 |
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50 |
| Workbench | 102 |
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104 |
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220 |
| Coil electric |
222 |
| Coil electric main |
224 |
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226 |
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228 |
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240 |
| Ball electricity |
242 |
| Ball electricity main |
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246 |
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248 |
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260 |
| Lifting table | 262 |
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264 |
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280 |
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282 |
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284 |
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290 |
| Front/ |
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294 |
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296 |
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302 |
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306 |
| Loading |
308 |
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402 |
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| Heated for controlling |
412 |
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502 |
| Air- |
504 |
| Air-float guide |
506 |
| Tension-compression sensor | 508 |
| Microgroove |
510 |
Following embodiment further illustrates the present invention in connection with above-mentioned accompanying drawing.
Embodiment
Below in conjunction with the accompanying drawings and the specific embodiments rub measurement device provided by the invention is described in further detail.
See also Fig. 1 and Fig. 2, the embodiment of the present invention provides a kind of rub measurement device 1, this rub measurement device 1 comprises a support system 10, one disc driving system 220, one ball drive system 240, one displacement regulating system 260, one angular adjustment system 280, one protection system 290, one loading system 30, one lubricating system 40 and a test macro 50, described support system 10 is positioned at the bottom of described rub measurement device 1, for carrying and fixing described disc driving system 220, ball drive system 240, displacement regulating system 260, angular adjustment system 280, protection system 290, loading system 30, lubricating system 40 and test macro 50, and the vibration producing when working for reducing this rub measurement device 1.Described displacement regulating system 260 is set directly in described support system 10, for regulating horizontal shift and the upper and lower displacement of described disc driving system 220.Described loading system 30 is positioned at the top of described displacement regulating system 260 and is connected with disc driving system 220 with described displacement regulating system 260 respectively, is used to this rub measurement device 1 that loading force is provided.Described disc driving system 220 is arranged at described displacement regulating system 260 tops and is slidably connected with described displacement regulating system 260, is used to this rub measurement device 1 that driving force is provided.Described protection system 290 is positioned at the right side of described disc driving system 220, and is connected with one end of described disc driving system 220, and travelling carriage is located on described test macro 50, is used to this rub measurement device 1 that protection is provided.Described ball drive system 240 is positioned at the inside of described protection system 290, during measurement described in ball drive system 240 contact with described disc driving system 220, be used to this rub measurement device 1 that driving force is provided.Described angular adjustment system 280 is connected with described ball drive system 240, for regulating the anglec of rotation of described ball drive system 240.Described test macro 50 is fixedly connected with between described protection system 290 and support system 10 and with described support system 10, for measuring the friction force of friction pair.Described lubricating system 40 is a detachable system, can independently be arranged on outside described support system 10, also can be fixedly installed in described support system 10, is used to this rub measurement device 1 that lubricating oil is provided.
This rub measurement device 1 integral body is a vertical structure, can, for measuring the friction, lubrication performance under low speed, can measure again the friction, lubrication performance under high speed (Entrainment Velocity is more than or equal to 100m/s).
The concrete structure of described support system 10 is not limit, as long as can play the effect of supporting and carrying.In the present embodiment, described support system 10 comprises a workbench 102 and a base 104, and wherein, this base 104 is fixedly installed on the table top of this workbench 102.The mode that described base 104 is fixed on this workbench 102 is not limit, as welded, be threaded etc.In the present embodiment, the part of described base 104 is fixedly installed on this workbench 102 by inlaying.Described workbench 102 adopts the materials processing with high anti-vibration performance to form, and in the present embodiment, described workbench 102 is a marble workbench.Described base 104 adopts the materials processing with higher-strength and stability to form, and in the present embodiment, described base 104 is a cast iron base.
The concrete structure of described displacement regulating system 260 is not limit, as long as can play the effect that regulates the relative position between described disc driving system 220 and ball drive system 240.In the present embodiment, described displacement regulating system 260 is by regulating upper and lower displacement and the horizontal position in-migration of described disc driving system 220 to adjust the relative position between described disc driving system 220 and ball drive system 240.Described displacement regulating system 260 comprises a lifting table 262 and a horizontal guide rail 264.Described lifting table 262 is directly arranged on the table top of described workbench 102, and arranges with described base 104 intervals.In the present embodiment, described lifting table 262 is bolted to connection on the table top of described workbench 102.Described lifting table 262 comprises a fixed part and a movable part, and described movable part is positioned at the top of described fixed part, can be driven by motor, thereby the high precision that realizes stroke 50mm moves up and down.Described horizontal guide rail 264 is arranged on the table top of movable part of described lifting table 262, and particularly, described horizontal guide rail 264 is secured by bolts on the table top of described lifting table 262.
The concrete structure of described loading system 30 is not limit, as long as can play the effect that loading force is provided for this rub measurement device 1.In the present embodiment, described loading system 30 is slided and is arranged on the horizontal guide rail 264 of described displacement regulating system 260.This loading system 30 comprises a support 302, a force cell 304, a stepper motor 306 and a loading spring 308.Wherein, described support 302 travelling carriages are located on described horizontal guide rail 264, and this support 302 can be free to slide towards a horizontal direction along described horizontal guide rail 264.Described loading spring 308 is fixedly connected on one end of described support 302, is used to this loading system 30 that loading spring power is provided.Described force cell 304 is fixedly installed on described disc driving system 220, and this force cell 304 and interval relative with described loading spring 308 arranges, and is positioned at same level position with described loading spring 308, for measuring the spring force of described loading.In the present embodiment, described force cell 304 is a tension-compression sensor.The direction that is subject to force direction and described loading force of described tension-compression sensor is consistent or contrary.The direction of described loading force is consistent with the bearing of trend of described horizontal guide rail 264.During loading, described loading spring 308 can slide to described force cell 304 directions along described horizontal guide rail 264 by described support 302 under the driving of described stepper motor 306.Described stepper motor 306 is connected with described loading spring 308, for driving described loading spring 308 to move horizontally.Described loading system 30 can realize the loading of power between 0 ~ 50N, can realize contact hertz stress between friction pair between 0 ~ 1GPa.
Described disc driving system 220 is set up on described support 302, can along described horizontal guide rail 264, be free to slide by described support 302.Particularly, described disc driving system 220 comprises a dish electricity main shaft 222, the electric main shaft anchor ear 224 of a dish, a dish axle 226 and a dish 228.Electric main shaft anchor ear 224 fixed covers of described dish are located at the outside surface of the electric main shaft 222 of described dish, for the protection of the electric main shaft 222 of described dish.Understandably, the electric main shaft anchor ear 224 of described dish is a selectable unit (SU).The electric main shaft anchor ear 224 of described dish is fixed together with described force cell 304.Between the electric main shaft 222 of described dish and described dish axle 226, be fixedly connected with, for driving the rotation of described dish axle 226.In the present embodiment, between the electric main shaft 222 of described dish and described dish axle 226, by internal and external threads, be fixedly connected with.Between described dish axle 226 and described dish 228, be fixedly connected with, for driving the rotation of described dish 228.In the present embodiment, between described dish axle 226 and described dish 228, also by internal and external threads, be fixedly connected with.During work, described dish electricity main shaft 222 first rotates with certain speed, drives described dish axle 226 to rotate, and further drives described dish 228 to rotate with target velocity.Described disc driving system 220 can utilize described horizontal guide rail 264, coordinates described loading system 30 to realize displacement in the horizontal direction and the loading of power; Also can utilize described lifting table 262 to regulate its upper and lower displacement.
Described ball drive system 240 comprises a ball electricity main shaft 242, a ball electricity main shaft anchor ear 244, a ball journal 246 and a ball 248.Described ball electricity main shaft anchor ear 244 fixed covers are located at the outside surface of described ball electricity main shaft 242, for the protection of described ball electricity main shaft 242.Understandably, described ball electricity main shaft anchor ear 244 is a selectable unit (SU).Between described ball electricity main shaft 242 and described ball journal 246, be fixedly connected with, for driving the rotation of described ball journal 246.In the present embodiment, between described ball electricity main shaft 242 and described ball journal 246, by screw thread, be fixedly connected with.Between described ball journal 246 and described ball 248, be fixedly connected with, for driving the rotation of described ball 248.In the present embodiment, between described ball journal 246 and described ball 248, also by screw thread, be fixedly connected with.During work, described ball electricity main shaft 242 first rotates with certain speed, drives described ball journal 246 to rotate, and further drives described ball 248 to rotate with target velocity.Ball 248 in described ball drive system 240 arranges near the dish 228 in described disc driving system 220.During work, described ball 248 is in contact with one another with described dish 228, and meanwhile, described ball 248 slides and/or force of rolling friction along rotation generation between described ball 248 and dish 228 of described dish axle 226 along rotation and the described dish 228 of described ball journal 246.
Described protection system 290, for the protection of described dish 228 and ball 248, prevents that described dish 228 and ball 248 from meeting accident when high-speed rotation and friction.The concrete structure of described protection system 290 is not limit, and in the present embodiment, described protection system 290 is a shell structure, comprises two blocks of front/rear plates 292, a base plate 294 and two blocks of side plates 296.The common accommodation space that forms of described front/rear plate 292, base plate 294 and side plate 296, protects described dish 228 and ball 248.Preferably, described front/rear plate 292 selects organic glass or tempered glass to make, and described side plate 296 and base plate 294 all select aluminium sheet to make.Understandably, described protection system 290 is an optional system.
The concrete structure of described angular adjustment system 280 is not limit, as long as can play the effect that regulates the anglec of rotation of ball 248 in described ball drive system 240.In the present embodiment, described angular adjustment system 280 comprises a friction pulley 284 and a worm screw 282.Described worm screw 282 is arranged on the side plate 296 of described protection system 290; and be connected with described ball drive system 240; be used for driving described ball electricity main shaft 242 and the 244 together rotations of ball electricity main shaft anchor ear; thereby drive the rotation of described ball journal 246 and ball 248, thereby reach the object of the anglec of rotation of adjusting described ball 248.Described friction pulley 284 is connected with the biside plate 296 in described protection system 290 respectively by two bolts; and arrange near the ball electricity main shaft anchor ear 244 in described ball drive system 240; can be used for locking described ball electricity main shaft 242 and ball electricity main shaft anchor ear 244, thus the position of fixing described ball journal 246 and ball 248.Described angular adjustment system 280 can further comprise an electronics inclinometer (not shown), and described electronics inclinometer can intuitively, accurately be read the anglec of rotation of described ball 248.
Rub measurement device of the prior art, the angle between its ball journal and dish axle is generally fixed as 90 degree, cannot regulate.Because there is certain area the contact region of ball and dish, on the diverse location of contact region, the inconsistent of direction will be caused cancelling each other of friction force inside, thereby produces the original reason error of friction measurement.And in the embodiment of the present invention, can be by described displacement regulating system 260 and angular adjustment system 280 by the axes intersect of described ball journal 246 and dish axle 226 in the card center of described dish 228, as shown in Figure 3, thereby the direction that guarantees ball dish contact region is consistent, and then the original reason error of eliminating or reducing friction while measuring, calculating and the process of argumentation that it is concrete are as follows:
Suppose that contact region is a circle spot, supposes that contact region radius is
, the radius of center, contact region dish 228 is R1, chooses respectively left hand edge point a, central point b and right hand edge point c in contact region.The angular velocity of supposing dish 228 is
, the angular velocity of ball 248 is
.When the axes intersect of described ball journal 246 and dish axle 226 is in card center O, described ball journal 246 and card the angle of cut while being α, a, b, 3 corresponding radiuses of a ball of c and dish radius all change to some extent.Therefore from following table, can find out, the ball dish linear velocity of diverse location is consistent, can realize pure rolling or sliding the rolling than unanimously in whole region, thereby the direction of whole ball dish contact region is consistent.
In addition, in prior art, generally ball is placed on bearing retainer, by the first driving bearing holder of motor, then drives the rotation of ball, like this, inevitably will between ball and bearing retainer, produce certain friction force, thereby bring Systematic Errors to friction measurement.And due to disc driving system described in the embodiment of the present invention 220 and ball drive system 240 respectively employing coil electric main shaft 222 and ball electricity main shaft 242 directly drives described dish 228 and balls 248, omit the intermediate transmission of bearing or belt, thereby avoided the generation of this Systematic Errors.
Described test macro 50 is fixedly installed on described base 104, and it comprises two fixture block supports 502, an air-float guide rail 504, at least one air-float guide rail slide block 506, a tension-compression sensor 508 and a microgroove bolt 510.
Described air-float guide rail 504 is directly arranged on described base 104.The mode that described air-float guide rail 504 is fixed on described base 104 is not limit.In the present embodiment, described air-float guide rail 504 is bolted and is arranged on described base 104.Described air-float guide rail slide block 506 travelling carriages are located on described air-float guide rail 504, can be free to slide along described air-float guide rail 504.Described ball drive system 240 is arranged on described air-float guide rail slide block 506 by described base plate 294, can move horizontally with described air-float guide rail slide block 506, and its moving direction is mutually vertical with the moving direction of described disc driving system 220.Described two fixture block support 502 fixed mounts are located on described air-float guide rail 504, and lay respectively at the both sides of described ball drive system 240, be used for limiting described ball drive system 240 and only move horizontally within the specific limits, thereby avoid it under high speed, to produce significantly vibration.Described microgroove bolt 510 is arranged in described two fixture block supports 502.Described tension-compression sensor 508 is fixed on described fixture block support 502 by described microgroove bolt 510, in order to measure the friction force between ball dish, records vibration regularity simultaneously.The pressure direction that described tension-compression sensor 508 is subject in measuring process is identical or contrary with the direction of described friction force, owing to having adopted air-float guide rail 504, its friction factor is very little, when measuring, can ignore, therefore, also approximately equal of the size of described pressure and the size of friction force.That is, utilize this tension-compression sensor 508 can directly read the friction value between described dish 228 and ball 248.In addition, the direction of this friction force recording and the direction of described loading force are mutually vertical.
Test macro of the prior art, generally adopts plain bearing, because plain bearing can produce larger friction force when working, therefore inevitably can in test process, produce systematic error.This test macro 50 has adopted air-float guide rail 504, has reduced the originally friction force when work of device, thus the systematic error while having reduced this device busy.In addition, test macro of the prior art, generally adopts torque sensor, although torque sensor is insensitive to the direction of friction force, torque sensor cannot be measured the friction force under high speed.This test macro 50 has adopted tension-compression sensor 508, thus the friction force size under measuring at a high speed.
Described lubricating system 40 is a detachable system independently.During work, can be connected in described rub measurement device 1, while not working, detachably get off.
Described lubricating system 40 comprises an oil storage cup 402, a peristaltic pump 404, an oil hose 406, a return hose 408 and an oil groove 410.Described lubricating system 40 can further comprise a heated for controlling temperature device 412.Described oil storage cup 402 is used to this lubricating system 40 fuel feeding.Described peristaltic pump 404 is used to this lubricating system 40 that power is provided.One end of described oil hose 406 is connected with described peristaltic pump 404, and the other end is for being delivered to oil the card of described dish 228.Described oil groove 410 is positioned at described protection system 290, for storing the oil falling from described dish 228.Described return hose 408 is connected between described oil groove 410 and oil storage cup 402, for the oil of oil groove 410 is carried and got back in oil storage cup 402.Described heated for controlling temperature device 412 is for heating oil and control oily temperature.During described lubricating system 40 work, first open described heated for controlling temperature device 412, oil is heated to test temperature, open again described peristaltic pump 404, drive described oil hose 406 that oil is sprayed onto to described Pan228 center, when described dish 228 High Rotation Speed, high centrifugal force throws away oil along card, sprawl whole card, thereby realize lubricated.The oil being thrown out of flows in described oil groove 410 along described side plate 296, then gets back in described oil storage cup 402 by described return hose 408, thereby forms lubrication oil supply circulation.
Described lubricating system 40 is for realizing stable the lubricating between at a high speed lower described ball 248 and dish 228.This lubricating system 40 is to utilize " oil spout " pattern to realize stable the lubricating between described ball 248 and dish 228, with respect to " immersion " of the prior art pattern, can more approach working condition.
Compared with prior art, rub measurement device provided by the invention, can be at contact hertz stress 1GPa, and Entrainment Velocity surpasses under 100m/s condition measures friction force; Can be by adjusting relative position between described dish and the ball original reason error when reducing friction measurement; The systematic error when mode that can be fixedly connected with described ball, dish by described electric main shaft and the mode that adopts air-float guide rail reduce friction measurement.Rub measurement device provided by the invention, can evaluate lubricant at lubricating property and friction and wear behavior at a high speed and under the harsh conditions of high temperature, for the design of the friction pairs such as bearing equipped at a high speed provides friction, lubrication parameter and technical basis.
The present invention also provides a kind of and utilizes above-mentioned rub measurement device 1 to measure the method for friction force, and it specifically comprises the following steps:
Step S1: the diameter of determining described dish 228 and ball 248;
Step S2: utilize described angular adjustment system 280 to make described ball 248 rotate to a predetermined angular;
Step S3: utilize described displacement regulating system 260 that described dish 228 is fit together with ball 248, and make the axis of described ball journal 246 and the axes intersect of dish axle 226 in the card center O of described dish 228;
Step S4: start described lubricating system 40, for the rubbing surface between described dish 228 and ball 248 provides lubrication oil supply circulation;
Step S5: start respectively described disc driving system 220 and ball drive system 240, described dish 228 and ball 248 are rotated with an initial velocity respectively;
Step S6: start described loading system 30, apply a predetermined loading force between described dish 228 and ball 248;
Step S7: regulate respectively described disc driving system 220 and ball drive system 240, described dish 228 and ball 248 are rotated with a predetermined speed respectively; And
Step S8: record the friction force between described dish 228 and ball 248 by described test macro 50.
In step S1, the diameter of described dish 228 and ball 248 can be selected according to actual needs.In the present embodiment, the diameter ratio of the diameter of described dish 228 and ball 248 is about 2:1, and wherein, the diameter of described dish 228 is about 25 millimeters, and the diameter of described ball 248 is about 12.5 millimeters.Understandably, described step S1 is an optional step.
In step S2, described predetermined angular refers to that the axis and of described ball journal 246 is parallel to the angle of cut between the plane of card of described dish 228.Described predetermined angular is greater than 0 degree and is less than 90 degree.Preferably, described predetermined angular is more than or equal to 15 degree and is less than or equal to 30 degree.In the present embodiment, described predetermined angular is 30 degree.
During concrete operations, first by described worm screw 282, described ball 248 is rotated to described predetermined angular, then by described friction pulley 284, described ball drive system 240 is fixing, thus the position of fixing described ball 248.
Step S3 specifically comprises following two steps:
Step S31: by described horizontal guide rail 264, described disc driving system 220 is moved horizontally, described dish 228 is fitted with described ball 248; And
Step S32: by described lifting table 262, described disc driving system 220 is moved up and down, make the axis of described ball journal 246 and the axis of described dish axle 226 just intersect at card center O.
Understandably, the order of described step S2 and step S3 can be changed mutually,, can first by described displacement regulating system 260, regulate described ball 248 and coil the relative position between 228, also can first by described angular adjustment system 280, regulate the angle between described ball journal 246 and dish axle 226.
As previously mentioned, when the axis of described ball journal 246 and the axis of described dish axle 226 do not intersect at card center, the direction of described ball dish contact region is inconsistent, thus the original reason error in the time of can producing friction measurement; And when the axis of described ball journal 246 and the axis of described dish axle 226 intersect at card center just, can guarantee that the direction of described ball dish contact region is consistent, and then the original reason error of eliminating or reducing friction while measuring.
In step S4, the process that starts described lubricating system 40 is: first open described heated for controlling temperature device 412, oil is heated to a predetermined temperature, then open described peristaltic pump 404, drive described oil hose 406 that oil is sprayed onto in the card of described dish 228 along a direction.Wherein, described distributive value and oil spout direction all can be adjusted according to actual needs.
In step S5, described initial velocity is between 1m/s ~ 50m/s, and in the present embodiment, described initial velocity is 5m/s.When described disc driving system 220 starts, the motor in described dish electricity main shaft 222 drives described dish axle 226 to rotate, and further drives described dish 228 to rotate with described initial velocity.Similarly, when described ball drive system 240 starts, the motor in described ball electricity main shaft 242 drives described ball journal 246 to rotate, and further drives described ball 248 to rotate with described initial velocity.
In step S6, the process that applies of described loading force is: first start described stepper motor 306, drive described loading spring 308 to move horizontally to described force cell 304, by the time after described loading spring 308 contacts with described force cell 304, power on described loading spring 308 passes to described disc driving system 220 by described force cell 304, is finally loaded between described dish 228 and ball 248.Described predetermined loading force can be selected according to actual needs.In the present embodiment, between described dish 228 and ball 248, contact hertz stress between 0GPa ~ 1GPa.
In step S7, described predetermined speed is the speed under actual condition or under simulated condition, is generally (as being more than or equal to 100m/s) at a high speed.Described predetermined speed is greater than described initial velocity.The predetermined speed of described dish 228 can be different from the predetermined speed of described ball 248.The predetermined speed of described dish 228 also can be identical with the predetermined speed of described ball 248.
In step S8, the numerical value of described friction force can directly be measured by the tension-compression sensor 508 in described test macro 50.Because described friction force can pass to described tension-compression sensor 508 by described protection system 290; or directly by described ball drive system 240, pass to described tension-compression sensor 508; apply a power identical with described direction or contrary and that size is identical to described tension-compression sensor 508; therefore the numerical value of, reading on described tension-compression sensor 508 and described friction force in the same size.
Further, by described tension-compression sensor 508, measuring the numerical value of described friction force, and utilize described force cell 304 to measure after the numerical value of described loading force, can utilize friction force computing formula to calculate the friction factor of friction pair in this device, thereby can evaluate the friction, lubrication characteristic of described lubricating oil.
Compared with prior art, friction measurement method provided by the invention, can be at contact hertz stress 1GPa, and Entrainment Velocity surpasses the friction force of measuring friction pair in described device under 100m/s condition; By adjusting relative position between described dish and the ball original reason error when reducing friction measurement; The systematic error when mode being fixedly connected with described ball, dish by described electric main shaft and the mode that adopts air-float guide rail reduce friction measurement.Friction measurement method provided by the invention, can evaluate lubricant at lubricating property and friction and wear behavior at a high speed and under the harsh conditions of high temperature, for the design of the friction pairs such as bearing equipped at a high speed provides friction, lubrication parameter and technical basis.
In addition, those skilled in the art also can do other and change in spirit of the present invention, and certainly, the variation that these are done according to spirit of the present invention, within all should being included in the present invention's scope required for protection.
Claims (10)
1. a rub measurement device, comprising:
Disc driving system, drives a disc spins by a dish axle;
Ball drive system, drives a ball to rotate by a ball journal;
Displacement regulating system, for regulating the relative position between described dish and ball;
Angular adjustment system, for regulating the angle between described dish axle and ball journal;
Loading system, for providing loading force between described dish and ball;
Lubricating system, for providing lubricating oil between described dish and ball; And
Test macro, measures the friction force between described dish and ball by a tension-compression sensor.
2. rub measurement device as claimed in claim 1, it is characterized in that, described disc driving system further comprises a dish electricity main shaft, between described dish electricity main shaft, dish axle and dish, is all fixedly connected with, and the rotation of the electric main shaft of described dish drives described dish to rotate with same angular velocity by described dish axle; Described ball drive system further comprises a ball electricity main shaft, between described ball electricity main shaft, ball journal and ball, is all fixedly connected with, and the rotation of described ball electricity main shaft drives described ball to rotate with same angular velocity by described ball journal.
3. rub measurement device as claimed in claim 1, is characterized in that, described angular adjustment system comprises a worm screw and a friction pulley; Described worm screw is for regulating the anglec of rotation of described ball, and described friction pulley is for the position of fixing described ball.
4. rub measurement device as claimed in claim 1, it is characterized in that, described displacement regulating system comprises a lifting table and a horizontal guide rail, described lifting table is for regulating the upper and lower displacement of described dish, described horizontal guide rail is fixedly installed on the table top of described lifting table, for regulating the horizontal shift of described dish.
5. rub measurement device as claimed in claim 4, is characterized in that, described loading system comprises a loading spring and a force cell; Described loading spring slides and is arranged on described horizontal guide rail, for provide loading force between described dish and ball; Described force cell and described loading spring are oppositely arranged and are fixedly installed on described disc driving system, the loading force providing for measuring described loading spring; The direction of described loading force is consistent with the bearing of trend of described horizontal guide rail.
6. rub measurement device as claimed in claim 5, is characterized in that, the direction of described loading force is vertical with the direction of described friction force.
7. rub measurement device as claimed in claim 1, it is characterized in that, described test macro further comprises an air-float guide rail and at least one air-float guide rail slide block, described air-float guide rail slide block slides and is arranged on described air-float guide rail, described ball drive system is directly or indirectly arranged on described air-float guide rail slide block, described tension-compression sensor obtains the friction force between described dish and ball by the pressure that described in sensing, the slip in the horizontal direction of ball drive system brings, and the direction of described pressure is consistent with the direction of described friction force or contrary.
8. rub measurement device as claimed in claim 1, is characterized in that, described lubricating system comprises an oil storage cup, a peristaltic pump, an oil hose, a return hose and an oil groove; Described oil storage cup is used to described lubricating system fuel feeding; Described peristaltic pump is used to described lubricating system that power is provided; Described oil hose is connected with described peristaltic pump, for oil being delivered to described Pan center; Described oil groove is for storing the oil falling from described dish; Described return hose is connected between described oil groove and oil storage cup, for the oil of described oil groove is carried and got back in described oil storage cup.
9. rub measurement device as claimed in claim 1; it is characterized in that; further comprise protection system; described protection system comprises front/rear plate, base plate and two side plates; described front/rear plate, base plate and two side plates surround a shell structure jointly, and described ball drive system supports by described protection system and is positioned at described shell structure.
10. rub measurement device as claimed in claim 1, is characterized in that, during measurement, the axes intersect of the axis of described ball journal and described dish axle is in the card center of described dish.
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| CN201310449208.7A CN103528945B (en) | 2013-09-27 | 2013-09-27 | Friction measurement device |
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| CN201310449208.7A CN103528945B (en) | 2013-09-27 | 2013-09-27 | Friction measurement device |
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| CN104198370A (en) * | 2014-09-19 | 2014-12-10 | 四川大学 | Intelligent measurement and control system of slide-roll tribology performance experiment table |
| CN104677764A (en) * | 2015-03-04 | 2015-06-03 | 中国石油大学(北京) | Friction wear test device |
| CN104990873A (en) * | 2015-06-22 | 2015-10-21 | 清华大学 | Method for online measuring friction chemical performance of lubricating interface |
| CN105223130A (en) * | 2015-11-03 | 2016-01-06 | 湖南工业大学 | The proving installation of friction factor and method of testing between adhesive tape and adhesive tape |
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| CN104677764A (en) * | 2015-03-04 | 2015-06-03 | 中国石油大学(北京) | Friction wear test device |
| CN104990873B (en) * | 2015-06-22 | 2017-11-28 | 清华大学 | The method that on-line measurement lubricates interface friction chemical property |
| CN104990873A (en) * | 2015-06-22 | 2015-10-21 | 清华大学 | Method for online measuring friction chemical performance of lubricating interface |
| CN106092874A (en) * | 2015-09-01 | 2016-11-09 | 北京林业大学 | A kind of measurement apparatus |
| CN106053334A (en) * | 2015-09-29 | 2016-10-26 | 北京林业大学 | Friction and pressurization detection test stand |
| CN105223130A (en) * | 2015-11-03 | 2016-01-06 | 湖南工业大学 | The proving installation of friction factor and method of testing between adhesive tape and adhesive tape |
| CN105223130B (en) * | 2015-11-03 | 2018-09-04 | 湖南工业大学 | The test device and test method of friction coefficient between adhesive tape and adhesive tape |
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| WO2018059105A1 (en) * | 2016-09-28 | 2018-04-05 | 清华大学 | Apparatus for measuring friction force of lubricant |
| CN106482881B (en) * | 2016-09-28 | 2018-10-16 | 清华大学 | Measure the device of lubricant frictional force |
| CN106442318A (en) * | 2016-10-28 | 2017-02-22 | 河北纳泰化工有限公司 | Lubricant friction force tester |
| CN106442318B (en) * | 2016-10-28 | 2023-07-25 | 河北纳泰化工有限公司 | Lubricant friction tester |
| CN108387509A (en) * | 2018-02-01 | 2018-08-10 | 合肥工业大学 | Rub force checking device under a kind of hot conditions |
| CN108387509B (en) * | 2018-02-01 | 2020-09-04 | 合肥工业大学 | Friction force detection device under high temperature condition |
| CN109521169B (en) * | 2018-11-29 | 2021-05-11 | 新昌县小布点农业发展有限公司 | Freshness degree detection equipment based on outer surface friction force of eggs |
| CN109521169A (en) * | 2018-11-29 | 2019-03-26 | 王艳玲 | A kind of freshness detection device based on egg outer surface frictional force |
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| CN112945555A (en) * | 2021-02-20 | 2021-06-11 | 青岛科技大学 | Vacuum reciprocating type heavy-load friction testing machine |
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