CN117405330A - Bearing operability verification test bed and bearing operability verification test method - Google Patents
Bearing operability verification test bed and bearing operability verification test method Download PDFInfo
- Publication number
- CN117405330A CN117405330A CN202311397813.4A CN202311397813A CN117405330A CN 117405330 A CN117405330 A CN 117405330A CN 202311397813 A CN202311397813 A CN 202311397813A CN 117405330 A CN117405330 A CN 117405330A
- Authority
- CN
- China
- Prior art keywords
- bearing
- moment
- loading
- verification test
- operability verification
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000012360 testing method Methods 0.000 title claims abstract description 84
- 238000012795 verification Methods 0.000 title claims abstract description 32
- 238000010998 test method Methods 0.000 title claims description 10
- 230000007246 mechanism Effects 0.000 claims abstract description 99
- 238000006073 displacement reaction Methods 0.000 claims abstract description 29
- 230000000712 assembly Effects 0.000 claims abstract description 17
- 238000000429 assembly Methods 0.000 claims abstract description 17
- 239000000872 buffer Substances 0.000 claims abstract description 15
- 229910000831 Steel Inorganic materials 0.000 claims description 25
- 239000010959 steel Substances 0.000 claims description 25
- 238000001228 spectrum Methods 0.000 claims description 23
- 238000000034 method Methods 0.000 claims description 20
- 230000005540 biological transmission Effects 0.000 claims description 12
- 230000008569 process Effects 0.000 claims description 11
- 230000008859 change Effects 0.000 claims description 7
- 238000013461 design Methods 0.000 claims description 6
- 230000000149 penetrating effect Effects 0.000 claims description 6
- 125000004122 cyclic group Chemical group 0.000 claims description 4
- 230000013011 mating Effects 0.000 claims description 3
- 238000009826 distribution Methods 0.000 abstract description 4
- 230000000052 comparative effect Effects 0.000 description 9
- 238000005070 sampling Methods 0.000 description 9
- 230000033001 locomotion Effects 0.000 description 4
- 238000003825 pressing Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 239000012160 loading buffer Substances 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000011056 performance test Methods 0.000 description 2
- 241000755266 Kathetostoma giganteum Species 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000002457 bidirectional effect Effects 0.000 description 1
- 238000007405 data analysis Methods 0.000 description 1
- 238000013480 data collection Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M5/00—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings
- G01M5/0041—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings by determining deflection or stress
- G01M5/005—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings by determining deflection or stress by means of external apparatus, e.g. test benches or portable test systems
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/04—Bearings
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Aviation & Aerospace Engineering (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention provides a bearing operability verification test bed, which comprises a supporting mechanism, a bearing arranged in the supporting mechanism, a load mechanism and a moment loading mechanism arranged in the bearing, wherein the load mechanism is arranged on the bearing; the load mechanism comprises a force arm and a loading sleeve, wherein one end of the force arm is connected with the force moment loading mechanism through a matched tool, and the other end of the force arm is connected with the loading sleeve; the bottom of the loading sleeve is provided with a shaft head, the inner bottom of the loading sleeve is provided with a plurality of displacement sensors, and the bottoms of the displacement sensors are contacted with the top of the shaft head. The bearing operability verification test bed is characterized by comprising a supporting mechanism, a load mechanism, a bearing, a matching tool, a moment loading mechanism and other detail parts. The parts can effectively simulate the running states of the hub bearing under different working conditions of the whole vehicle, so that the control performance of the hub bearing can be accurately estimated. Meanwhile, the stability and the reliability of the test bed can be further increased through staggered distribution of the plurality of first linear bearing assemblies and the buffer assemblies.
Description
Technical Field
The invention relates to the technical field of bearing tests, in particular to a bearing operability verification test bed and a bearing operability verification test method.
Background
The hub bearing is a very important component for bearing and providing accurate guidance for the rotation of the hub, and it is subjected to both axial and radial loads. With the development of automobile technology, people have higher requirements on the automobile operability besides the requirements on the automobile dynamic property, the automobile economy and the automobile braking property. The steering stability of an automobile mainly refers to the steering performance of a steering system of the automobile and the stability of an automobile body during steering of the automobile, and when the automobile is actually driven, if the rigidity of a bearing is poor, a steering hysteresis phenomenon can occur. Steering wheel angle of rotation is in place and tire angle feedback is retarded. Generally, a suspension system with good operability is soft and comfortable during normal running, and becomes very hard during turning, so that good support is provided for an automobile, and the roll of the automobile is reduced, and therefore, the automobile has higher control limit. The hub bearing has a critical effect on this as a load bearing and component part that provides accurate guidance for the rotation of the hub.
At present, various simulation tests are required to be carried out on the automobile hub bearing before the automobile hub bearing is put into use, so that performance tests such as sealing, service life and rigidity of a hub bearing unit are inspected. However, the conventional stiffness test is to test the amount of deformation of the bearing with a certain forward moment applied to the bearing.
Although the performance test method can effectively ensure the basic quality of the bearing, the control performance of the bearing in operation cannot be effectively identified, and further the automobile control performance is complained to be poor when the whole automobile is tested by road or the automobile is used by a customer, so that a hub bearing control performance verification test method is needed to effectively identify the bearing control performance under various working condition operation states of a product on the whole automobile, and avoid the abnormal product from flowing into the market, so that economic loss and influence on the reputation of a company are avoided.
Disclosure of Invention
The invention provides a bearing operability verification test bed and a bearing operability verification test method, which solve the problems mentioned in the background art.
The technical scheme of the invention is realized as follows:
the bearing operability verification test bed comprises a supporting mechanism, a bearing arranged in the supporting mechanism, a load mechanism and a moment loading mechanism, wherein the load mechanism and the moment loading mechanism are arranged in the bearing;
the load mechanism comprises a force arm and a loading sleeve, wherein one end of the force arm is connected with the force moment loading mechanism through a matched tool, and the other end of the force arm is connected with the loading sleeve; the bottom of the loading sleeve is provided with a shaft head, the inner bottom of the loading sleeve is provided with a plurality of displacement sensors, and the bottom of each displacement sensor is contacted with the top of the shaft head;
the bearing sleeve is arranged outside the shaft head, and the supporting mechanism is arranged outside the bearing in a sleeved mode to limit and fix the bearing.
Further, the moment loading mechanism comprises a bearing assembly, wherein the bearing assembly comprises an upper bearing plate, a lower bearing plate and at least one middle bearing plate, and the middle bearing plate is positioned between the upper bearing plate and the lower bearing plate;
further, a plurality of groups of buffer components are arranged in the moment loading mechanism, and each buffer component comprises a support shaft penetrating through a plurality of bearing plates and a spring sleeved outside the support shaft and positioned between the adjacent bearing plates; wherein, the both ends of back shaft are respectively with upper and lower loading board fixed connection, and the centre of back shaft and well loading board sliding connection.
Further, a plurality of groups of first linear bearing assemblies are further arranged in the moment loading mechanism, and each first linear bearing assembly comprises a first bearing rod and a first linear bearing sliding on the first bearing rod; the two ends of the first bearing rod are fixedly connected with the upper bearing plate and the lower bearing plate respectively, the first linear bearing is fixed on the middle bearing plate, and the middle bearing plate is in sliding connection with the outside of the first bearing rod through the first linear bearing.
Further, the moment loading mechanism further comprises a second linear bearing assembly, wherein the second linear bearing assembly comprises a second bearing rod penetrating through the lower bearing plate and the top of the second linear bearing rod is fixed with the middle bearing plate, and a second linear bearing which is fixed on the lower bearing plate and is in sliding connection with the second bearing rod.
Further, the matching tool comprises an upper tool and a lower tool, and the upper tool and the lower tool are aligned and fixed through a first fixing screw; the bottom of the second bearing rod is fixed with the top of the upper tool, the lower tool is in a frame design, the end part of the force arm extends into the frame of the lower tool, a steel ball for bearing the end part of the force arm is respectively arranged on the upper part and the lower part of the lower tool, and a fixing bolt for locking the steel ball is connected with the bottom of the lower tool through threads.
Further, a flange is arranged on the side part of the loading sleeve, the flange is sleeved at the other end of the force arm, and the loading sleeve is fixed with the force arm through the flange; the bottom of the loading sleeve is provided with a plurality of second fixing screws, and the second fixing screws penetrate through the shaft head and are in threaded fixation with the bottom of the loading sleeve.
Further, the supporting mechanism comprises a base and a steering knuckle, wherein a plurality of support posts are arranged on the base, and each support leg of the steering knuckle is correspondingly arranged on the support post; the support posts are fixed with the support legs of the steering knuckle through bolts or nuts.
Further, a mandrel is arranged in the steering knuckle, the middle of the mandrel penetrates through the shaft head, one end of the mandrel extends to the bottom of the steering knuckle, and the other end of the mandrel extends to the loading sleeve and is fixed through a nut thread.
The bearing operability verification test method is applied to the bearing operability verification test bed and comprises the following steps:
s1, assembling rigidity test equipment: the method comprises the steps of installing a bearing sleeved with a knuckle on a load mechanism, sequentially connecting a moment arm, a load sleeve and a shaft head, and then connecting the moment arm, the load sleeve and the shaft head with the moment load mechanism through a matched tool, wherein the bearing is used for applying a circulating load to the bearing;
s2, formulating a rigidity test load spectrum: collecting vehicle information parameters, and formulating a test load spectrum according to the vehicle information parameters, wherein the test load spectrum is used for simulating different working conditions of vehicle running;
s3, testing based on a test load spectrum: the condition that the bearing receives moment in the frequent turning steering process of the automobile is simulated, specifically:
a. the distance from the loading sleeve to the arm is the radius length of the simulated wheel, the stress moment loading mechanism is applied to the position of the steel ball at the end part of the arm and pressure or tension is applied to simulate the stress at the radius of the tire, and the precise transmission of the torque is realized by utilizing the universal characteristic of the spherical stress of the steel ball;
b. inputting a load spectrum in a rigid equipment program;
c. and starting a test, and automatically recording the displacement change result of the bearing along with the change of the moment in the cyclic moment loading process by the equipment and forming a curve.
The beneficial effect that this application provided technical scheme brought:
1. the bearing operability verification test bed is characterized by comprising a supporting mechanism, a load mechanism, a bearing, a matching tool, a moment loading mechanism and other detail parts. The parts can effectively simulate the running states of the hub bearing under different working conditions of the whole vehicle, so that the control performance of the hub bearing can be accurately estimated. Meanwhile, the stability and the reliability of the test bed can be further increased through staggered distribution of the plurality of first linear bearing assemblies and the buffer assemblies.
2. According to the bearing operability verification test method, the rigidity test bed is used for applying the circulating torque to the bearing, and the deformation of the bearing in the whole circulating torque is obtained through the displacement sensor, so that the operability of the automobile in the frequent reversing running process is simulated.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic view of a bearing operability verification test stand according to the present invention;
FIG. 2 is a schematic diagram of a torque loading buffer assembly and a mating tool according to the present invention;
FIG. 3 is a schematic view of the load mechanism, the mating tooling and the support mechanism of the present invention;
FIG. 4 is a schematic diagram of a torque loading buffer assembly according to the present invention;
FIG. 5 is a schematic view of the structure of the supporting mechanism of the present invention;
FIG. 6 is a schematic structural diagram of the fitting tool of the present invention;
FIG. 7 is a schematic illustration of the spindle head of the present invention changing the stressed position during testing;
FIG. 8 is a graph of load time versus load moment;
fig. 9 is a graph of the displacement variation resulting from the moment loading process.
In the figure: 100 load mechanisms, 110 force arms, 120 loading sleeves, 121 flanges, 122 second fixing screws, 130 shaft heads and 140 displacement sensors;
200 supporting mechanisms, 210 bases, 211 struts, 220 knuckles, 221 grooves and 222 mandrels;
300 moment loading mechanism, 310 bearing assembly, 311 upper bearing plate, 312 middle bearing plate, 313 lower bearing plate, 320 buffer assembly, 321 supporting shaft, 322 spring, 330 first linear bearing assembly, 331 first bearing rod, 332 first linear bearing, 340 second linear bearing assembly, 341 second bearing rod, 342 second linear bearing;
400 bearings;
500, 510 upper tools, 520 lower tools, 530 first fixing screws, 540 fixing bolts and 550 steel balls.
Detailed Description
The technical solutions of the present invention will be clearly and completely described in conjunction with the embodiments of the present invention, and it is apparent that the described embodiments are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 1 to 7, a bearing operability verification test stand includes a support mechanism 200, a bearing 400 disposed in the support mechanism 200, a load mechanism 100 disposed in the bearing 400, and a moment loading mechanism 300;
the supporting mechanism 200 is used as a foundation for fixedly supporting the bearing 400, the load mechanism 100 in the bearing 400 is used for limiting the bearing 400 on the supporting mechanism 200, in addition, the moment loading mechanism 300 is fixed on one side of the load mechanism 100, and the stress of the moment loading mechanism 300 can be transmitted to the bearing 400 of the supporting mechanism 200 through the load mechanism 100, so that the actual stress working condition of the bearing 400 is simulated.
The load mechanism 100 comprises a force arm 110 and a loading sleeve 120, wherein one end of the force arm 310 is connected with the moment loading mechanism 300 through a matching tool 500, and the other end of the force arm 310 is connected with the loading sleeve 120; the bottom of the loading sleeve 120 is provided with a shaft head 130, the inner bottom of the loading sleeve 120 is provided with a plurality of displacement sensors 140, and the bottom of the displacement sensors 140 is contacted with the top of the shaft head 130; the bearing 400 is sleeved outside the shaft head 130, and the supporting mechanism 200 is sleeved outside the bearing 400 to limit and fix the bearing 400.
Because the shaft head 130 is sleeved by the bearing 400, the two are tightly contacted, when the moment loading mechanism 300 receives external loading moment, the moment loading mechanism transmits the moment to the loading sleeve 120 through the matched tool 500 and the moment arm 310, and the loading sleeve 120 is fixed with the shaft head 130, so that the moment is transmitted to the bearing 400 outside the shaft head 130; by arranging a plurality of displacement sensors 140 at the inner bottom of the loading sleeve 120 and limiting the bottom of the displacement sensors 140 to be in contact with the top of the spindle head 130, the displacement generated by the moment of the bearing 400 can be measured by the displacement sensors 140 at the top of the spindle head 130, so that the bearing 400 simulates the real stress working condition of the bearing 400 and the control performance of the bearing 400 is detected.
In some embodiments, the moment loading mechanism 300 includes a carrier assembly 310, where the carrier assembly 310 includes an upper carrier plate 311, a lower carrier plate 313, and at least one middle carrier plate 312, and the middle carrier plate 312 is located between the upper and lower carrier plates;
the moment loading mechanism 300 is used as a main mechanism for moment transmission, by providing an upper bearing plate 311 and a lower bearing plate 313 as basic balance components of the moment loading mechanism 300, and a middle bearing plate 312 is used as moment loading components of the moment loading mechanism 300, wherein a plurality of middle bearing plates 312 can be provided, and the middle bearing plates 312 can generate displacement between the upper bearing plate 311 and the lower bearing plate 313 so as to form moment motion.
In some embodiments, in order to ensure that the middle bearing plate 312 in the moment loading mechanism 300 can stably realize moment transmission, a plurality of groups of buffer assemblies 320 are disposed in the moment loading mechanism 300, where the buffer assemblies 320 include a support shaft 321 penetrating through the plurality of bearing plates, and a spring 322 sleeved outside the support shaft 311 and located between adjacent bearing plates; wherein, two ends of the supporting shaft 311 are fixedly connected with the upper and lower bearing plates respectively, and the middle of the supporting shaft 311 is slidably connected with the middle bearing plate 310.
Because the upper bearing plate 311 and the lower bearing plate 313 are balance components, the main motion components generate moment through the middle bearing plate 312, the upper bearing plate 311 and the lower bearing plate 313 need to be kept still, the middle bearing plate 312 needs to be displaced between the upper bearing plate 311 and the lower bearing plate 313, and two ends of the supporting shaft 311 in the buffer assembly 320 are fixedly connected with the upper bearing plate and the lower bearing plate respectively, so that the upper bearing plate 311 and the lower bearing plate 313 can be limited. Further, by arranging the springs 322 between the adjacent bearing plates, the upper bearing plate 311 and the lower bearing plate 313 will not move, so that the up-down displacement of the middle bearing plate 312 can drive the springs 322 to stretch and compress to form a pressing force and a pulling force, and the middle bearing plate 312 can also be reset by using the springs 322, so that the middle bearing plate 312 can continuously displace and transmit the moment under the condition that the moment does not disappear. The spring 322 may be a rectangular coil spring, and the main purpose is that the rectangular design of the rectangular coil spring makes the contact between the rectangular coil spring and the bearing plate more compact and reliable, so as to avoid the unstable stress caused by less contact between the traditional round spring and the bearing plate.
In order to improve the balance and stability of the vertical displacement of the centering and carrying plate 312, in some embodiments, a plurality of groups of first linear bearing assemblies 330 are further disposed in the moment loading mechanism 300, where the first linear bearing assemblies 330 include a first bearing rod 331 and a first linear bearing 332 sliding on the first bearing rod 331; the two ends of the first bearing rod 331 are fixedly connected with the upper and lower bearing plates respectively, the first linear bearing 332 is fixed on the middle bearing plate 312, and the middle bearing plate 312 is slidably connected outside the first bearing rod 331 through the first linear bearing 332.
The first bearing rod 331 in the first linear bearing assembly 330 further defines the limit of the upper bearing plate 311 and the lower bearing plate 313, so that the two are always kept at the same distance. The first linear bearing 332 outside the first bearing rod 331 is fixed in the middle bearing plate 312, and the first bearing rod 331 slides with the first linear bearing 332, so that the middle bearing plate 312 is slidably connected outside the first bearing rod 331 through the first linear bearing 332, and the first linear bearing 332 slides in the first bearing rod 331 to form a power-assisted guiding effect, so that the stability of the movement of the middle bearing plate 312 is further improved.
In addition, the first linear bearing assemblies 330 are staggered with the supporting shaft 321; the staggered design makes the moment applied to the middle bearing plate 312 in different directions balanced, and no offset or skew is generated, so that the balance of the middle bearing plate 312 in the moment transmission process is further improved.
Since the moment transmission of the moment loading mechanism 300 is achieved by the up-down displacement of the middle bearing plate 312 of the bearing assembly 310, and the positions of the upper bearing plate 311 and the lower bearing plate 313 of the bearing assembly 310 are limited so as not to be displaced, when the bearing assembly 310 itself receives moment, the displacement of the middle bearing plate 312 cannot be achieved, and in order to ensure the moment transmission, the following embodiments are implemented by taking the bearing assembly 310, the first linear bearing assembly 330 and the buffer assembly 320 as a whole: the moment loading mechanism 300 further includes a second linear bearing assembly 340, and the second linear bearing assembly 340 includes a second bearing rod 341 penetrating the lower bearing plate 313 and having a top fixed to the middle bearing plate 312, and a second linear bearing 342 fixed to the lower bearing plate 313 and slidably coupled to the second bearing rod 341.
When the bearing assembly 310, the first linear bearing assembly 330 and the buffer assembly 320 are used as an integral bearing mechanism, the integral bearing mechanism is displaced on the second linear bearing assembly 340 under the condition of moment, because the position of the second bearing rod 341 is unchanged, the top of the second bearing rod 341 is fixed with the middle bearing plate 312, the lower bearing plate 313 slides on the second bearing rod 341 through the second linear bearing 342, the integral bearing mechanism slides along the second bearing rod 341 by utilizing the lower bearing plate 313 during the downward movement, the middle bearing plate 312 slides on the first bearing rod 331 due to the unchanged position of the second bearing rod 341, the distance between the middle bearing plate 312 and the lower bearing plate 313 is changed, so as to form an axial moment, and the axial moment is transmitted to the bearing 400 through the second bearing rod 341, the matched tool 500 and the loading sleeve 120, so as to realize the stress working condition simulating the axial moment of the bearing.
Wherein the second linear bearing assembly 340 corresponds to the middle of the carrier assembly 310; since the first linear bearing assemblies 330 and the supporting shafts 321 are staggered on the bearing assembly 310, in order to avoid the balance of the torque transmitted by the bearing assembly 310 to the second linear bearing assemblies 340, the second linear bearing assemblies 340 are correspondingly arranged in the middle of the bearing assembly 310, and the stability of torque transmission is maintained.
In some embodiments, the matching fixture 500 includes an upper fixture 510 and a lower fixture 520, where the upper fixture and the lower fixture are aligned and fixed by a first fixing screw 530; the bottom end of the second bearing rod 341 is fixed to the top of the upper tool 510, the lower tool 520 is in a frame design, the end of the arm of force 110 extends into the frame of the lower tool 520, a steel ball 550 receiving the end of the arm of force 110 is respectively arranged up and down inside the lower tool 520, and a fixing bolt 540 locking the steel ball 550 is connected with the bottom of the lower tool 520 in a threaded manner.
In order to simulate the reality of bearing stress, a steel ball 550 is respectively arranged on the upper and lower sides of one end of the arm 110 corresponding to the lower tool 520, the lower tool 520 is indirectly connected with the arm 110, in order to avoid the steel ball 550 from sliding on the arm 110, the inner part of the lower tool 520, the top of the fixing bolt 540, and the upper and lower sides of the arm 110 are respectively provided with a ball groove (not marked in the figure) corresponding to the upper and lower two steel balls 550, and the steel ball 550 can be prevented from sliding in the ball groove through adaptation. In addition, in order to increase the tightness between the force arm 110 and the lower tool 520, the steel ball 550 is pre-tightened by the fixing bolt 540 at the bottom of the lower tool 520, and then the torque loading mechanism 300 realizes accurate transmission of torque by utilizing the universal characteristic of the spherical stress of the steel ball 550.
Wherein the position of the torque loading mechanism 300 is rotated after the test of the primary bearing 400 is completed, specifically: the spindle head 130 is used as a center of a circle, the second fixing screw 122 is adjusted and detached, the loading sleeve 120 is detached from the spindle head 130, the direction of the spindle head 130 is manually rotated, the installation of the subsequent force arm 110 is correspondingly adjusted to the point B or the point C (the test point is shown in fig. 7), then the loading sleeve 120 is reinstalled and the second fixing screw 122 is fastened, the spindle head 130, the loading sleeve 120 and the force arm 110 are fixedly connected again, tension or pressure is applied to the moment loading mechanism 300 at the top of the moment arm 110 at the changing point, the position of the changing loading point is considered to have a random relative position relation between the distribution of two rows of steel balls in the bearing 400 and the axial loading direction, the relative position relation between the axial loading direction and the installation direction of the spindle head has a great influence on a rigidity test result, and the mode fully simulates the bearing 400 stress condition of an automobile in the frequent reversing running process.
As shown in fig. 1, the second bearing rod 341 is vertically arranged, the arm 110 is horizontally arranged, and the two bearing rods 341 and the arm 110 form a vertical angle, after being connected by the matching tool 500, when the second bearing rod 341 generates an axial moment, the horizontal arrangement of the arm 100 generates a moment to generate an axial moment to the bearing 400 through the loading sleeve 120, so that by the arrangement, the moment loading mechanism 300 can simultaneously generate a bidirectional moment transmission to the bearing 400 through the matching of the matching tool 500 and the loading mechanism 100, and fully simulate the stress state of the bearing 400 under a real working condition.
In some embodiments, a flange 121 is disposed at a side of the loading sleeve 120, the flange 121 is sleeved at the other end of the arm 110, and the loading sleeve 120 is fixed with the arm 110 through the flange 121; the bottom of the loading sleeve 120 is provided with a plurality of second fixing screws 122, and the second fixing screws 122 penetrate through the shaft heads 130 and are in threaded fixation with the bottom of the loading sleeve 120.
The loading sleeve 110 can form a stable connection relation with the arm 110 and the shaft head 130 through the flange 121 and the second fixing screw 122, when the moment loading mechanism 300 transmits moment through the matching tool 500, the loading sleeve 110, the arm 110 and the shaft head 130 on the loading mechanism 100 cannot cause unstable moment transmission due to loose connection.
In some embodiments, the supporting mechanism 200 includes a base 210 and a knuckle 220, where a plurality of struts 211 are disposed on the base 210, and each leg of the knuckle 220 is correspondingly mounted on the strut 211; the support post 211 is fastened to each leg of the knuckle 220 by bolting or screwing with a nut.
The main purpose of the support mechanism 200 is to provide a balanced test platform for the bearing 400, and the base 210 can fix each leg of the knuckle 220 through a plurality of support posts 211, so as to ensure that the bearing 400 inside the knuckle 220 can be kept stable.
In some embodiments, the knuckle 220 has a groove 221 therein, wherein the exterior of the bearing 400 fits within the groove 221. The grooves 221 are arranged to provide safe and reliable limiting conditions for the bearing 400, and the bearing 400 is surrounded by the grooves 221, so that the bearing 400 cannot deviate in the test process.
In some embodiments, a spindle 222 is disposed in the knuckle 220, the middle of the spindle 222 penetrates through the spindle head 130 and the groove 221, one end of the spindle 222 extends to the bottom of the knuckle 220, and the other end extends to the loading sleeve 120 and is fixed by a nut thread.
The spindle 222 mainly holds the knuckle 220, the bearing 400 and the spindle head 130 tightly, so that the bearing 400 is tested safely and reliably. The mandrel 222 is a flat-head mandrel, the butt end of which is limited at the bottom of the knuckle 220, and the other end of which is locked by a nut, so that the knuckle 220, the bearing 400 and the shaft head 130 can be in close contact with each other, thereby realizing axial pre-tightening and avoiding the loosening.
Example 1
Referring to fig. 8-9, a bearing operability verification test method, using a bearing operability verification test stand, comprises the steps of:
s1, assembling rigidity test equipment: the bearing 400 sleeved with the knuckle 220 is arranged on a rigid test bed, the moment arm 110, the loading sleeve 120 and the shaft head 130 are connected in sequence, and then the moment loading mechanism 300 is arranged for applying a circulating axial load to the bearing 400;
s2, formulating a rigidity test load spectrum: collecting vehicle information parameters, and formulating a test load spectrum according to the vehicle information parameters, wherein the test load spectrum is used for simulating different working conditions of vehicle running;
s3, testing based on a test load spectrum:
pressing the double-row angular contact ball bearing into the steering knuckle 220 and then into the spindle head 130, and placing the spindle 222 into the spindle head 130 to be locked by a nut;
the method comprises the steps of fixedly mounting a steering knuckle 220 on a base 210, fixedly connecting a loading sleeve 120 with a shaft head 130 through bolts, mounting a force arm 110 on the side surface of the loading sleeve 130 through a flange 121, fixing the other end of the force arm 131 in a matched tool 110 through a first fixing screw 540, and placing a displacement sensor 140 on the end surface of the shaft head 130 to test the deformation of a bearing 400 when the bearing 400 receives circulating torque;
the moment loading mechanism 300 comprises a bearing assembly 310, a buffer assembly 320, a first linear bearing assembly 330, and a second linear bearing assembly 340, wherein the bearing assembly 310 comprises an upper bearing plate 311, a middle bearing plate 312, and a lower bearing plate 313; the buffer component 320 adopts a multi-layer spring structure design, wherein springs on two sides are respectively responsible for the force output and buffer function of pulling and pressing;
the displacement sensor 140 is fixed by a magnetic meter frame (not shown in the figure), specifically, the displacement sensor 140 is first locked on the magnetic meter frame by a screw (one end of the magnetic meter is originally used for fixing a test meter), then the measuring head of the displacement sensor 140 is aligned to the symmetry plane of the spindle nose 130, and finally the magnetic meter frame is fixed on the base 210 by a magnet switch.
In some embodiments, the test load spectrum formulated in step S2 is as follows, so as to simulate the situation that the bearing receives moment during the frequent turning and steering of the automobile:
| step No. | Load rate/N/s | Sampling frequency/Hz | moment/kN.m |
| 1 | 400 | 100 | 0 to 2 |
| 2 | 400 | 100 | 2 to 0 |
| 3 | 400 | 100 | 0 to-2 |
| 4 | 400 | 100 | -2 to 0 |
The relation between the loading time and the loading moment is shown in fig. 6;
in some embodiments, the "test based on test load spectrum" in step S3 is:
a. one end of the arm 110 is preloaded with a steel ball 550 of 12-20mm placed at the lower tooling 520 through a fixing bolt 2540, the other end of the arm 110 is connected to a loading sleeve 120 of the loading mechanism 100 through a flange 121, the distance from the loading sleeve 120 to the arm 110 is the radius length of a simulated wheel, the stress moment loading mechanism 300 is applied by pressing or pulling the steel ball 550, and the stress is applied by simulating the radius of a tire; the precise transmission of the moment is realized by utilizing the universal characteristic of the spherical stress of the steel ball 550, in addition, the size of the loading mechanism 300 matched with the steel ball 550 is increased by excessively large steel ball 550, the cost is increased, and the insufficient bearing of the steel ball 550 can not effectively simulate the stress at the radius of the tire;
b. inputting a load spectrum in a rigid equipment program;
c. the test was started and the apparatus automatically recorded the results of the displacement changes of the bearing with the moment changes during cyclic moment loading and formed a curve (see figure 9 for the graph).
d. After the test according to the direction A is finished, the relative positions of the moment loading mechanism 300 in different axial loading directions at the end part of the moment arm 110 are changed to perform the test for 2 times, and the test is performed three times in total, specifically, the axle head is subjected to trisection according to an included angle of 120 degrees (the test point is shown in fig. 7), the test positions are the point A (0 degree), the point B (120 degrees) and the point C (240 degrees), the change of the loading point positions is realized by considering that the relative position relation between the distribution of two rows of steel balls 550 in the bearing 400 and the axial loading direction is random, and the relative position relation between the axial loading direction and the installation direction of the axle head 130 has great influence on the rigidity test result.
1) The corresponding rigidity of each step load is more than 6000N.m/°;
2) The stiffness value A1 at any load loading, the stiffness value A2 at return, the difference between A1 and A2 (the smaller the difference, the better the handling).
3) Any load point stiffness value takes the average of three load positions A, B, C.
According to the bearing operability verification test method, the rigidity test bed is used for applying the circulating torque to the bearing, and the deformation of the bearing in the whole circulating torque is obtained through the displacement sensor 133, so that the operability of the automobile in the frequent reversing running process is simulated.
The bearing 400 is applied with a circulating torque through the rigid test bed, and the deformation of the bearing 400 in the whole circulating torque is monitored through the displacement sensor 140, so that the bearing stress condition of an automobile in the process of frequent reversing running is simulated, and the aim of verifying the reliability and durability of the bearing is fulfilled. The implementation mode of the technical scheme mainly comprises the following steps: firstly, assembling rigidity test equipment, mounting a bearing 400 on a knuckle 220 of a supporting mechanism 200, connecting a load mechanism 100 and applying a cyclic load to the bearing 400 by using a matching tool 500 to connect a moment loading mechanism 300; then, a test load spectrum is formulated and used for simulating load conditions under different working conditions; and finally, testing based on a test load spectrum, and recording the deformation amount of the bearing when the bearing is subjected to the circulating moment, so as to evaluate the reliability and durability of the bearing. Through the realization of the technical scheme, the control process of the automobile in actual running can be fully simulated, the reliability and durability of the bearing 400 can be objectively evaluated, the product quality and reliability of the bearing 400 are improved, more reliable bearing products are provided for automobile manufacturers, and the competitiveness of the whole automobile industry chain is improved.
Comparative example 1
The procedure was as in example 1, wherein the test load spectrum established in step S2 was as follows:
| step No. | Load rate/N/s | Sampling frequency/Hz | moment/kN.m |
| 1 | 600 | 100 | 0 to 2 |
| 2 | 600 | 100 | 2 to 0 |
| 3 | 600 | 100 | 0 to-2 |
| 4 | 600 | 100 | -2 to 0 |
Comparative example 2
The procedure was as in example 1, wherein the test load spectrum established in step S2 was as follows:
comparative example 3
The procedure was as in example 1, wherein the test load spectrum established in step S2 was as follows:
| step No. | Load rate/N/s | Sampling frequency/Hz | moment/kN.m |
| 1 | 400 | 50 | 0 to 2 |
| 2 | 400 | 50 | 2 to 0 |
| 3 | 400 | 50 | 0 to-2 |
| 4 | 6400 | 50 | -2 to 0 |
Comparative example 4
The procedure was as in example 1, wherein the test load spectrum established in step S2 was as follows:
| step No. | Load rate/N/s | Sampling frequency/Hz | moment/kN.m |
| 1 | 400 | 150 | 0 to 2 |
| 2 | 400 | 150 | 2 to 0 |
| 3 | 400 | 150 | 0 to-2 |
| 4 | 400 | 150 | -2 to 0 |
In summary, the disadvantage of comparative example 1 is that the loading rate is too high, resulting in limited test time and failure to detect the change in performance of the tire after long-term use. This may result in an inability to accurately evaluate the reliability and durability of the bearing, thereby affecting product quality. The disadvantage of comparative example 2 is that the loading rate is too low, resulting in too long a test time, and the performance change of the tire after long-term use cannot be detected in a concentrated manner. This may increase test costs and cycle time, reduce efficiency, and fail to meet actual production requirements. The disadvantage of comparative example 3 is that the sampling frequency is too small, and the deformation condition of the load test point cannot be found accurately by data analysis, so that the performance of the bearing under the actual working condition cannot be estimated accurately. The disadvantage of comparative example 4 is that too high a sampling frequency results in too large a data collection volume, increasing the complexity of data processing and analysis. At the same time, too high a sampling frequency may result in redundancy and duplication of data, which is not required for the handling performance evaluation of the hub bearing. In addition, high sampling frequencies also increase the time and cost of the test and may not be practical for practical production. Therefore, comparative example 4 requires appropriate adjustment, and reasonable sampling frequency is selected to balance the problems of test effect and resource utilization.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.
Claims (10)
1. A bearing operability verification test stand, comprising a supporting mechanism (200), a bearing (400) arranged in the supporting mechanism (200), a load mechanism (100) arranged in the bearing (400) and a moment loading mechanism (300); the method is characterized in that:
the load mechanism (100) comprises a force arm (110) and a loading sleeve (120), wherein one end of the force arm (310) is connected with the moment loading mechanism (300) through a matching tool (500), and the other end of the force arm (310) is connected with the loading sleeve (120); the bottom of the loading sleeve (120) is provided with a shaft head (130), the inner bottom of the loading sleeve (120) is provided with a plurality of displacement sensors (140), and the bottom of each displacement sensor (140) is contacted with the top of the corresponding shaft head (130);
the bearing (400) is sleeved outside the shaft head (130), and the supporting mechanism (200) is sleeved outside the bearing (400) to limit and fix the bearing.
2. The bearing operability verification test stand of claim 1, wherein the moment loading mechanism (300) comprises a carrier assembly (310), the carrier assembly (310) comprising an upper carrier plate (311), a lower carrier plate (313), and at least one middle carrier plate (312), the middle carrier plate (312) being located between the upper and lower carrier plates.
3. The bearing operability verification test stand according to claim 2, wherein a plurality of groups of buffer assemblies (320) are arranged in the moment loading mechanism (300), the buffer assemblies (320) comprise supporting shafts (321) penetrating through a plurality of bearing plates, and springs (322) sleeved outside the supporting shafts (311) and positioned between adjacent bearing plates; wherein, both ends of the supporting shaft (311) are respectively fixedly connected with the upper bearing plate and the lower bearing plate, and the middle of the supporting shaft (311) is in sliding connection with the middle bearing plate (310).
4. The bearing operability verification test stand of claim 2, wherein a plurality of sets of first linear bearing assemblies (330) are further provided in the moment loading mechanism (300), the first linear bearing assemblies (330) including first bearing bars (331), and first linear bearings (332) sliding on the first bearing bars (331); the two ends of the first bearing rod (331) are fixedly connected with the upper bearing plate and the lower bearing plate respectively, the first linear bearing (332) is fixed on the middle bearing plate (312), and the middle bearing plate (312) is in sliding connection outside the first bearing rod (331) through the first linear bearing (332).
5. The bearing operability verification test stand of claim 2, wherein said moment loading mechanism (300) further comprises a second linear bearing assembly (340), said second linear bearing assembly (340) comprising a second bearing rod (341) penetrating the lower carrier plate (313) and having a top fixed to the middle carrier plate (312), and a second linear bearing (342) fixed to the lower carrier plate (313) and slidably connected to the second bearing rod (341).
6. The bearing operability verification test stand of claim 5, wherein the mating tooling (500) comprises an upper tooling (510) and a lower tooling (520), the upper and lower tooling being aligned and fixed by a first set screw (530); the bottom of the second bearing rod (341) is fixed with the top of the upper tool (510), the lower tool (520) is in a frame design, the end part of the force arm (110) extends into the frame of the lower tool (520), steel balls (550) for supporting the end part of the force arm (110) are respectively arranged in the upper and lower parts of the lower tool (520), and the bottom of the lower tool (520) is in threaded connection with a fixing bolt (540) for locking the steel balls (550).
7. The bearing operability verification test stand according to claim 1, wherein a flange (121) is arranged at the side part of the loading sleeve (120), the flange (121) is sleeved at the other end of the force arm (110), and the loading sleeve (120) is fixed with the force arm (110) through the flange (121); the bottom of the loading sleeve (120) is provided with a plurality of second fixing screws (122), and the second fixing screws (122) penetrate through the shaft head (130) and are fixed with the bottom of the loading sleeve (120) in a threaded mode.
8. The bearing operability verification test stand of claim 1, wherein the supporting mechanism (200) comprises a base (210) and a knuckle (220), wherein a plurality of struts (211) are provided on the base (210), and each leg of the knuckle (220) is correspondingly mounted on the strut (211); the support post (211) is fixed with each leg of the knuckle (220) through a bolt connection or a nut thread.
9. The bearing operability verification test stand of claim 8, wherein a spindle (222) is disposed in the knuckle (220), a middle of the spindle (222) penetrates through the spindle head (130), one end of the spindle extends to the bottom of the knuckle (220), and the other end of the spindle extends to the loading sleeve (120) and is fixed through nut threads.
10. Bearing operability verification test method characterized in that the bearing operability verification test stand according to any one of claims 1 to 9 is applied, comprising the steps of:
s1, assembling rigidity test equipment: the method comprises the steps of installing a bearing (400) sleeved with a knuckle (220) on a load mechanism (100), sequentially connecting a moment arm (110), a loading sleeve (120) and a shaft head (130), and then connecting the moment arm with the moment loading mechanism (300) through a matching tool (500) for applying a circulating load to the bearing (400);
s2, formulating a rigidity test load spectrum: collecting vehicle information parameters, and formulating a test load spectrum according to the vehicle information parameters, wherein the test load spectrum is used for simulating different working conditions of vehicle running;
s3, testing based on a test load spectrum: the condition that the bearing receives moment in the frequent turning steering process of the automobile is simulated, specifically:
a. the distance from the loading sleeve (120) to the force arm (110) is the radius length of the simulated wheel, the stress moment loading mechanism (300) is applied to the position of the steel ball (550) at the end part of the force arm (110) and pressure or tension is applied to simulate the stress at the radius of the tire, and the precise transmission of the moment is realized by utilizing the universal characteristic of the spherical stress of the steel ball (550);
b. inputting a load spectrum in a rigid equipment program;
c. and starting a test, and automatically recording the displacement change result of the bearing along with the change of the moment in the cyclic moment loading process by the equipment and forming a curve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311397813.4A CN117405330B (en) | 2023-10-25 | 2023-10-25 | Bearing operability verification test bed and bearing operability verification test method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311397813.4A CN117405330B (en) | 2023-10-25 | 2023-10-25 | Bearing operability verification test bed and bearing operability verification test method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN117405330A true CN117405330A (en) | 2024-01-16 |
| CN117405330B CN117405330B (en) | 2024-06-04 |
Family
ID=89499602
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311397813.4A Active CN117405330B (en) | 2023-10-25 | 2023-10-25 | Bearing operability verification test bed and bearing operability verification test method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117405330B (en) |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201331403Y (en) * | 2008-12-26 | 2009-10-21 | 洛阳轴研科技股份有限公司 | Moment rigidity tester for hub bearing unit |
| JP2012251818A (en) * | 2011-06-01 | 2012-12-20 | Nsk Ltd | Preload measuring method for multi-row angular ball bearing, device implementing the same, and preload-guaranteed multi-row angular ball bearing |
| CN103048126A (en) * | 2012-12-12 | 2013-04-17 | 北京工业大学 | Loading device for load-unbalance experiment of static-pressure rotary table |
| CN106092582A (en) * | 2016-08-12 | 2016-11-09 | 浙江万向精工有限公司 | Hub bearing unit torque rigidity test device and method |
| CN106092583A (en) * | 2016-08-12 | 2016-11-09 | 浙江万向精工有限公司 | Hub bearing unit torque rigidity test system and method |
| CN207007516U (en) * | 2017-07-10 | 2018-02-13 | 洛阳铭昊测控科技有限公司 | A kind of automobile bearing testing machine |
| CN210571275U (en) * | 2019-08-28 | 2020-05-19 | 湖北新火炬科技有限公司 | Radial impact clamp for automobile hub bearing unit |
| CN111537229A (en) * | 2020-04-21 | 2020-08-14 | 西安交通大学 | Bearing seat device capable of measuring running parameters of bearing at different positions |
| CN214251563U (en) * | 2021-03-01 | 2021-09-21 | 中信戴卡股份有限公司 | Knuckle system power test loading arm |
| CN115931615A (en) * | 2022-12-21 | 2023-04-07 | 万向钱潮股份公司 | Hub bearing unit three-axis fretting wear testing machine and testing method |
| CN116007915A (en) * | 2022-12-13 | 2023-04-25 | 陕西煤业新型能源科技股份有限公司科研中心分公司 | Rotary machinery vibration fault diagnosis device |
-
2023
- 2023-10-25 CN CN202311397813.4A patent/CN117405330B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201331403Y (en) * | 2008-12-26 | 2009-10-21 | 洛阳轴研科技股份有限公司 | Moment rigidity tester for hub bearing unit |
| JP2012251818A (en) * | 2011-06-01 | 2012-12-20 | Nsk Ltd | Preload measuring method for multi-row angular ball bearing, device implementing the same, and preload-guaranteed multi-row angular ball bearing |
| CN103048126A (en) * | 2012-12-12 | 2013-04-17 | 北京工业大学 | Loading device for load-unbalance experiment of static-pressure rotary table |
| CN106092582A (en) * | 2016-08-12 | 2016-11-09 | 浙江万向精工有限公司 | Hub bearing unit torque rigidity test device and method |
| CN106092583A (en) * | 2016-08-12 | 2016-11-09 | 浙江万向精工有限公司 | Hub bearing unit torque rigidity test system and method |
| CN207007516U (en) * | 2017-07-10 | 2018-02-13 | 洛阳铭昊测控科技有限公司 | A kind of automobile bearing testing machine |
| CN210571275U (en) * | 2019-08-28 | 2020-05-19 | 湖北新火炬科技有限公司 | Radial impact clamp for automobile hub bearing unit |
| CN111537229A (en) * | 2020-04-21 | 2020-08-14 | 西安交通大学 | Bearing seat device capable of measuring running parameters of bearing at different positions |
| CN214251563U (en) * | 2021-03-01 | 2021-09-21 | 中信戴卡股份有限公司 | Knuckle system power test loading arm |
| CN116007915A (en) * | 2022-12-13 | 2023-04-25 | 陕西煤业新型能源科技股份有限公司科研中心分公司 | Rotary machinery vibration fault diagnosis device |
| CN115931615A (en) * | 2022-12-21 | 2023-04-07 | 万向钱潮股份公司 | Hub bearing unit three-axis fretting wear testing machine and testing method |
Non-Patent Citations (1)
| Title |
|---|
| 胡晓辉: "角接触球轴承套圈沟位置的测量分析及改进_胡晓辉", 《轴承》, no. 2015, 31 December 2015 (2015-12-31), pages 59 - 63 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN117405330B (en) | 2024-06-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105699214B (en) | A kind of reverse micro move fatigue rig and test method | |
| CN103196754B (en) | Bending test device for semi-floating drive axle, and test method of same | |
| CN106950139B (en) | Friction and wear testing machine for joint bearing and hinge | |
| CN113218659B (en) | Rolling mill bearing fault diagnosis and life evaluation simulation test bed | |
| CN101832836A (en) | Dynamic calibration device of drum reaction braking checkout stand | |
| CN104457668B (en) | Portable axletree shaft-diameter measuring instrument | |
| CN110726636A (en) | Four-axis centering adjustment system and method for biaxial tensile testing machine | |
| CN117405330B (en) | Bearing operability verification test bed and bearing operability verification test method | |
| CN201673013U (en) | Dynamic calibration device of roller reaction type brake tester | |
| CN109752124A (en) | A kind of automobile hub bearing riveting pretightning force detection method | |
| CN107101816B (en) | Semi-floating semi-axis composite loading fatigue test stand | |
| CN207600339U (en) | A kind of novel driven wheel of differential pitch circle bounce gauge | |
| CN104833290B (en) | Power transmission shaft reverses the detection method and system in gap | |
| CN110726637B (en) | Centering adjustment device and centering adjustment method | |
| CN113447279A (en) | Be used for axle housing braking to twist reverse bench test device | |
| CN211179398U (en) | Coaxiality adjusting device for testing machine | |
| CN211179397U (en) | Fatigue testing machine capable of adjusting coaxiality | |
| CN112525404A (en) | Ball pin assembly torsion test marking device and test method | |
| CN110836830B (en) | Fatigue testing machine capable of adjusting coaxiality and load chain centering adjustment method | |
| CN110567718A (en) | Rolling bearing radial dynamic stiffness testing device based on piezoelectric actuator | |
| CN211179395U (en) | Centering adjusting device | |
| US20220316992A1 (en) | Loading system and test equipment for automobile chassis simulation road test | |
| CN209513284U (en) | A kind of pillar rotating torque detection device | |
| CN106092583A (en) | Hub bearing unit torque rigidity test system and method | |
| CN202133548U (en) | Loading device for oversize rotating disk bearing performance testing machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |