CN203856882U - High-speed ball bearing with integral monitoring component - Google Patents
High-speed ball bearing with integral monitoring component Download PDFInfo
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- CN203856882U CN203856882U CN201420279860.9U CN201420279860U CN203856882U CN 203856882 U CN203856882 U CN 203856882U CN 201420279860 U CN201420279860 U CN 201420279860U CN 203856882 U CN203856882 U CN 203856882U
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- retainer
- sensor
- magnet
- disk body
- cover plate
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- 238000012544 monitoring process Methods 0.000 title claims abstract description 24
- 230000005284 excitation Effects 0.000 abstract description 10
- 239000000463 material Substances 0.000 description 6
- 230000009471 action Effects 0.000 description 5
- 229910000906 Bronze Inorganic materials 0.000 description 3
- 229910052790 beryllium Inorganic materials 0.000 description 3
- ATBAMAFKBVZNFJ-UHFFFAOYSA-N beryllium atom Chemical compound [Be] ATBAMAFKBVZNFJ-UHFFFAOYSA-N 0.000 description 3
- 239000010974 bronze Substances 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 240000008168 Ficus benjamina Species 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000003745 diagnosis Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
Abstract
The utility model relates to a high-speed ball bearing with an integral monitoring component, belonging to the technical field of bearings and monitoring thereof. A ball cavity, a blind hole and a step hole are formed in a retainer; the retainer is riveted with an excitation magnet embedded in the step hole through a rivet; step shafts are arranged at two ends of an inner ring; step holes are formed in two ends of an outer ring; a chuck body is arranged on the step shafts or in the step holes; a sensor is arranged on the side wall of an annular groove of each chuck body; a circuit board and a cover plate are separately arranged on two sides of the chuck body; an energy harvester is arranged between the chuck body and the cover plate; an excited magnet is riveted in the center of the energy harvester and is arranged in a guide hole in the chuck body in a sleeving manner. The high-speed ball bearing with the integral monitoring component has the advantage that a self-energizing sensing and monitoring function is realized and real-time online monitoring can be realized in truth sense without changing the structure of the installing device; the structure and the excitation scheme of the energy harvester are reasonable, the guide hole is used for preventing the harvester from torsional pendulum, the excitation magnet rotating along with the retainer is used for exciting, so that the high-speed cylindrical roller bearing is high in reliability, large in generation amount and wide in valid speed band and is suitable for high rotation speed occasions.
Description
Technical field
The utility model belongs to bearing and monitoring technical field thereof, is specifically related to a kind of high-speed ball bearing of belt body monitoring assembly.
Background technique
Bearing is a kind of typical mechanical basic part, has application extremely widely in fields such as machinery, vehicle, Aero-Space, steamer and the energy; But bearing is also one of the most flimsy part in rotary machine, 30% of rotating machinery fault is to be caused by bearing failure.Therefore, the status monitoring of bearing and Incipient Fault Diagnosis have caused people's great attention.The on-line monitoring of bearing state has progressively become the indispensable technology in field such as high-rating generator, steamer, high ferro and aircraft, and the index of required monitoring comprises such as temperature, vibration, rotating speed and noise etc.Early stage bearing monitoring system is mainly external hanging type, and one of its drawback is distant between sensor and signal source, belongs to non-contacting indirect measurement, therefore error is larger.In recent years, people have proposed again multi-form Embedded Monitoring System in succession, this method can solve measuring accuracy and accuracy problem, but need to change structure or its integrity of relevant device, so that installation sensing and monitoring system, the problems such as this not only easily causes that the stress of equipment component is concentrated also cannot realize on the equipment of some complex structures or limited space; The most key, in the time that monitoring system need to be rotated with bearing inner race or outer ring, inconvenience is by line powered, and employing powered battery is very short service time.Therefore, current bearing monitoring system is all also non real-time, non-contact measurement indirectly substantially, is difficult to obtain timely and accurately the running state of bearing.
For solving the powerup issue of the rotation monitoring systems such as bearing, people have proposed the rotary piezoelectric generating device of various ways, its principle is directly to utilize the mode of encouraging coupling by magnetic that relatively rotates between axle and bearing support to encourage piezoelectric vibrator vibrating power-generation, and the maximum drawback of this mode of operation generator is to be only applicable to more slow-revving situation; In the time that rotating speed is higher, between rotary magnet and piezoelectric vibrator end magnet overlapping time extremely short, piezoelectric vibrator is difficult to obtain enough kinetic energy makes its generation vibrate and generate electricity.
Summary of the invention
The utility model provides a kind of high-speed ball bearing with integrated monitoring assembly, existing in the time that rotating speed is higher in actual applications to solve existing bearing monitoring system, between rotary magnet and piezoelectric vibrator end magnet overlapping time extremely short, piezoelectric vibrator is difficult to obtain enough kinetic energy makes it produce the problem of vibrating and generating electricity.
The technological scheme that the utility model is taked is: comprise inner ring, ball, retainer one and retainer two, outer ring, described retainer one and retainer two are provided with the ball-type chamber for ball is installed, for inlaying blind hole and the shoulder hole of exciting magnet, retainer one and retainer two and be embedded in retainer one and the shoulder hole of retainer two in exciting magnet pass through rivet, the two ends of inner ring are provided with multidiameter shaft, the two ends of outer ring are provided with shoulder hole, on described multidiameter shaft or in shoulder hole, by interference fit, disk body is housed, the both sides of disk body are respectively equipped with heavy chamber and annular groove, diapire in the middle of heavy chamber and annular groove is provided with pilot hole and wire guide, sensor one and sensor two or sensor three and sensor four are installed on the sidewall of annular groove, circuit board and cover plate are arranged on the side that is provided with annular groove and heavy chamber on disk body by screw respectively, described cover plate is provided with heavy chamber, between cover plate and disk body, be crimped with metallic film, be placed on the metallic film at the heavy chamber of disk body and the heavy chamber place of cover plate and form energy accumulator by being bonded with piezoelectric film, the center riveted joint of this energy accumulator has excited magnet, excited magnet is socketed in pilot hole, described excited magnet equates respectively with radius and the turning radius thereof of exciting magnet, the each energy accumulator and the sensor one that are placed on same disk body are connected with circuit board with sensor two or the sensor three wire group excessively different with sensor four-way.
The utility model has the advantages that novel structure, bearing self has self energizing sensor monitoring function, as independently standarized component use, without the structure that changes its erection unit, can realize real time on-line monitoring truly; Energy accumulator structure and exciting magnet configuration parameter are determined rationally and are adopted pilot hole to prevent that energy accumulator from rocking, therefore reliability is high, generated energy is large; Utilize the exciting magnet excitation energy accumulator rotating with retainer, effectively speed belt wide, can be used for high rotating speed occasion.
Brief description of the drawings
Fig. 1 is the section of structure of a preferred embodiment of the utility model;
Fig. 2 is the A-A view of Fig. 1;
Fig. 3 is the B-B view of Fig. 1;
Fig. 4 is the assembly structure schematic diagram of bearing main body part;
Fig. 5 is the structural representation of retainer;
Fig. 6 is the structural representation of disk body;
Fig. 7 is the configuration relation schematic diagram of exciting magnet and excited magnet;
Fig. 8 be the utility model different determine angle than time beam on the graph of relation of the suffered active force of magnet and corner ratio;
Fig. 9 is the utility model drive factor, maximum force and the graph of relation of determining angle ratio;
Figure 10 is the utility model structural coefficient and the when graph of relation of radius ratio of thickness.
Embodiment
As shown in Fig. 1～Fig. 6, comprise inner ring 1, ball 2, retainer 1 and retainer 23 ', outer ring 4, described retainer 1 and retainer 23 ' be provided with the ball-type chamber 31 for ball 2 is installed, for inlaying blind hole 32 and the shoulder hole 33 of exciting magnet C2, exciting magnet C2 in the shoulder hole 33 of retainer 1 and retainer 23 ' and be embedded in retainer 1 and retainer 23 ' passes through rivet, the two ends of inner ring 1 are provided with multidiameter shaft 11, the two ends of outer ring 4 are provided with shoulder hole 41, on described multidiameter shaft 11 or in shoulder hole 41, by interference fit, disk body 7 is housed, the both sides of disk body 7 are respectively equipped with heavy chamber 71 and annular groove 72, heavy chamber 71 is provided with pilot hole 74 and wire guide 75 with the diapire 73 in the middle of annular groove 72, sensor one S1 and sensor two S2 or sensor Three S's 3 and sensor four S4 are installed on the sidewall of annular groove 72, circuit board B and cover plate 5 are arranged on the side that is provided with annular groove 72 and heavy chamber 71 on disk body 7 by screw respectively, described cover plate 5 is provided with heavy chamber 51, between cover plate 5 and disk body 7, be crimped with metallic film 6, be placed on the metallic film 6 at the heavy chamber 71 of disk body 7 and 51 places, heavy chamber of cover plate 5 and form energy accumulator A by being bonded with piezoelectric film 8, the center riveted joint of this energy accumulator A has excited magnet C1, excited magnet C1 is socketed in pilot hole 74, described excited magnet C1 equates respectively with radius and the turning radius thereof of exciting magnet C2, the each energy accumulator A and sensor one S1 that are placed on same disk body 7 are connected with circuit board B by different wire groups with sensor four S4 with sensor two S2 or sensor Three S's 3.
In working procedure, in the time that inner ring 1 and outer ring 4 relatively rotate, and the relatively-stationary energy accumulator A in inner ring 1 or outer ring 4 and excited magnet C1 and retainer 3 and 3 ' and exciting magnet C2 between produce relative rotation, thereby change the axial force between excited magnet C1 and exciting magnet C2, make energy accumulator A produce cyclic bending distortion and convert mechanical energy to electric energy, the electric energy generating is sensing and monitoring system power supply after conversion treatment.In the utility model, prevent that by pilot hole 74 energy accumulator A from rocking, therefore can obtain larger generating capacity and higher reliability simultaneously.
According to mechanical knowledge, when the stationary object that quality is M is subject to after external force F action time t, its speed obtaining is that v=Ft/M, kinetic energy are E=(Ft)
2/ (2M).Obviously,, in the time that other condition is identical, when the action time of power is too short, object can be because gained energy shortage be to overcome still transfixion of inertial force.Encouraging based on magnetic in the rotary piezoelectric generator of coupling excitation, the action time of excitation force F is two and relatively rotates the overlapping time of magnet and increase and shorten with rotating speed, and in the time that rotating speed is too high, energy accumulator A will can effectively not encouraged.Therefore, the action time of increase excitation force or reduction relative rotation speed can effectively increase the external energy that energy accumulator A obtains.In the utility model, ball 2 and retainer 1 and retainer 23 ' and inner ring 1 and outer ring 4 between relative rotation speed n1 be about the λ of relative rotation speed n2 between inner ring 1 and outer ring 4
n=n1/n2=r/R doubly, therefore in the situation that other condition is identical, in the utility model, the endurance of active force is the λ of the action time of power when exciting magnet C2 is placed in to direct-drive on inner ring 1 or outer ring 4
t=1/ λ
ndoubly, wherein, r and R are respectively the radius of exciting magnet C2 and the turning radius at center thereof to=R/r.Therefore, utilize the exciting magnet C2 excitation energy accumulator A rotating with retainer 3 and 3 ' in the utility model, the kinetic energy obtaining is the λ utilizing while exciting magnet C2 direct-drive being installed on inner ring 1 or outer ring 4
e=(R/r)
2doubly, thus effectively speed belt wide, be more suitable for the occasion that rotating speed is higher.
In the utility model, for improving the generated energy of energy accumulator A, be placed in close installation of opposite pole of two exciting magnet C2 of same shaft section, be placed in the axial pole configuration opposite direction of adjacent exciting magnet C2 on two circumference of same cross section, and be placed in bearing the same side retainer 1 or retainer 23 ' on the quantity n of exciting magnet C2 should meet following formula,
Wherein, r and R are respectively the radius of exciting magnet C2 and the turning radius at center thereof; Or determine angle than meeting
wherein Q1 is two of the exciting magnet C2 angles between the crossing tangent line in bearing gyration center place, and Q2 is the angle between the line of two adjacent exciting magnet C2 centers and its gyration center.
For improving the generated energy of energy accumulator A, when other condition is determined, should improve as far as possible the amount of deformation of energy accumulator A and be excited number of times, improve amplitude and the excitation number of times of suffered excitation force, and should make the excited magnet C1 on energy accumulator A bear attraction force and repulsive force alternately, therefore the configuration mode of the magnetic pole of exciting magnet C2 is: be placed in the opposite pole of two exciting magnet C2 of same shaft section near installing, be placed in the axial pole configuration opposite direction of adjacent exciting magnet C2 on two circumference of same cross section; In addition,, in the time that bearing inner race 1 and outer ring 4 relatively rotate one week, the electric energy that single energy accumulator A produces can be expressed as:
Wherein C
ffor the free capacitance of energy accumulator A, V
g=η F is the off load voltage that energy accumulator A generates, and η is the voltage coefficient relevant with energy accumulator A yardstick and material, h=nF
2be called drive factor, λ=C
fη
2/ 2 are called structural coefficient, and n is single retainer 3 or 3 ' quantity of upper exciting magnet C2.Obviously,, in the time that other condition is determined, can improve voltage and electric energy by the quantity n and the structural coefficient λ that improve directed force F, exciting magnet C2; Wherein, the quantity n of exciting magnet C2 encourages number of times and amount of force two aspects to affect the power generation characteristics of energy accumulator A by change.The actual conditions that are space distribution according to the working principle of the utility model ball bearing and magnetic field, arbitrary excited magnet C1 is subject to the effect of multiple exciting magnet C2 simultaneously, and the size of total force F depends on determines angle ratio
wherein
for two of the exciting magnet C2 angles between the crossing tangent line in bearing gyration center place, Q2=2 π/n is the angle between the line of two adjacent exciting magnet C2 centers and its gyration center, r and R are respectively the radius of exciting magnet C2 and the turning radius at center thereof, can will determine angle than the function that converts exciting magnet C2 quantity n to thus,
further research shows, exists the different best angles of determining to make the suffered active force of energy accumulator A, voltage and electric energy maximum than k; In the time getting k=1～1.5, the scope of exciting magnet C2 quantity n is
time, the electric energy obtaining and voltage are all larger, wherein drive factor be not less than its peaked 1/2.
Fig. 8 provided different determine angle than time excited magnet C1 suffered directed force F with corner than the test curve of j=Q3/Q1, wherein Q3 is excited magnet C1 and a certain exciting magnet C2 overlapping rear turned over corner completely, is the position relationship between excited magnet C1 and each exciting magnet C2 therefore corner characterizes than j.Fig. 8 explanation, determine angle when different, the suffered exciting magnet C2 of excited magnet C1 active force big or small and the number of times difference encouraging.Active force amplitude and drive factor with determine angle than the relation curve of k as shown in Figure 9, obviously, in the time getting k=1.0～1.5, gained voltage and electric energy are all larger, drive factor be greater than its peaked 1/2.
In the utility model, for improving the generating capacity of energy accumulator A self, the material of metallic film 6 is beryllium bronze, the material of piezoelectric film 8 is PZT4, and the span that piezoelectric film 8 thickness and the span of the Thickness Ratio β of energy accumulator A are the ratio α of the radius in the radius of 0.5< β <0.7, piezoelectric film 8 and the heavy chamber 71 of disk body 7 is 0.5< α <0.7.
The utility model adopts the energy accumulator A of circular piezoelectric film 8 and metallic film 6 bonding structures, when the radius in the heavy chamber 71 of energy accumulator A thickness and disk body 7 is given timing, the thickness of piezoelectric film 8 and radius excessive or too small all can make energy accumulator A generating capacity reduce, in reality, existing best piezoelectric film 8 thickness to make the generated energy of energy accumulator A than the radius of β and piezoelectric film 8 with the ratio α of the radius in the heavy chamber 71 of disk body 7 with energy accumulator A total thickness is structural coefficient maximum.After the material parameter of metallic film 6 and piezoelectric film 8 is determined, can further try to achieve the relation of generated energy or structural coefficient λ and Thickness Ratio β and radius ratio α.The material of metallic film 6 of the present utility model is beryllium bronze, and the material of piezoelectric film 8 is PZT4, its structural coefficient and thickness when radius ratio relation as shown in figure 10.According to Figure 10, the better parameter area that the utility model is formed energy accumulator A by beryllium bronze and PZT4 is 0.5< β <0.7,0.5< α <0.7.
Claims (1)
1. the high-speed ball bearing with integrated monitoring assembly, comprise inner ring, ball, retainer one and retainer two, outer ring, it is characterized in that: described retainer one and retainer two are provided with the ball-type chamber for ball is installed, for inlaying blind hole and the shoulder hole of exciting magnet, retainer one and retainer two and be embedded in retainer one and the shoulder hole of retainer two in exciting magnet pass through rivet, the two ends of inner ring are provided with multidiameter shaft, the two ends of outer ring are provided with shoulder hole, on described multidiameter shaft or in shoulder hole, by interference fit, disk body is housed, the both sides of disk body are respectively equipped with heavy chamber and annular groove, diapire in the middle of heavy chamber and annular groove is provided with pilot hole and wire guide, sensor one and sensor two or sensor three and sensor four are installed on the sidewall of annular groove, circuit board and cover plate are arranged on the side that is provided with annular groove and heavy chamber on disk body by screw respectively, described cover plate is provided with heavy chamber, between cover plate and disk body, be crimped with metallic film, be placed on the metallic film at the heavy chamber of disk body and the heavy chamber place of cover plate and form energy accumulator by being bonded with piezoelectric film, the center riveted joint of this energy accumulator has excited magnet, excited magnet is socketed in pilot hole, described excited magnet equates respectively with radius and the turning radius thereof of exciting magnet, the each energy accumulator and the sensor one that are placed on same disk body are connected with circuit board with sensor two or the sensor three wire group excessively different with sensor four-way.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420279860.9U CN203856882U (en) | 2014-05-28 | 2014-05-28 | High-speed ball bearing with integral monitoring component |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420279860.9U CN203856882U (en) | 2014-05-28 | 2014-05-28 | High-speed ball bearing with integral monitoring component |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203856882U true CN203856882U (en) | 2014-10-01 |
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ID=51606734
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420279860.9U Expired - Fee Related CN203856882U (en) | 2014-05-28 | 2014-05-28 | High-speed ball bearing with integral monitoring component |
Country Status (1)
| Country | Link |
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| CN (1) | CN203856882U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103982539A (en) * | 2014-05-28 | 2014-08-13 | 浙江师范大学 | High-speed ball bearing with integrated monitoring assembly |
| CN111237339A (en) * | 2020-01-14 | 2020-06-05 | 燕山大学 | Magnetic rolling bearing capable of reducing balance radial force of gear pump and service life calculation method |
-
2014
- 2014-05-28 CN CN201420279860.9U patent/CN203856882U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103982539A (en) * | 2014-05-28 | 2014-08-13 | 浙江师范大学 | High-speed ball bearing with integrated monitoring assembly |
| CN103982539B (en) * | 2014-05-28 | 2017-01-11 | 浙江师范大学 | High-speed ball bearing with integrated monitoring assembly |
| CN111237339A (en) * | 2020-01-14 | 2020-06-05 | 燕山大学 | Magnetic rolling bearing capable of reducing balance radial force of gear pump and service life calculation method |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141001 Termination date: 20150528 |
|
| EXPY | Termination of patent right or utility model |