CN114321188A - Low friction torque bearing set and torque standard machine applying same - Google Patents
Low friction torque bearing set and torque standard machine applying same Download PDFInfo
- Publication number
- CN114321188A CN114321188A CN202111638060.2A CN202111638060A CN114321188A CN 114321188 A CN114321188 A CN 114321188A CN 202111638060 A CN202111638060 A CN 202111638060A CN 114321188 A CN114321188 A CN 114321188A
- Authority
- CN
- China
- Prior art keywords
- bearing
- rotating shaft
- magnet
- force
- pressure
- 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
- 238000007789 sealing Methods 0.000 claims description 26
- 238000005096 rolling process Methods 0.000 claims description 20
- 239000012530 fluid Substances 0.000 claims description 16
- 230000000694 effects Effects 0.000 abstract description 3
- 235000017166 Bambusa arundinacea Nutrition 0.000 description 5
- 235000017491 Bambusa tulda Nutrition 0.000 description 5
- 241001330002 Bambuseae Species 0.000 description 5
- 235000015334 Phyllostachys viridis Nutrition 0.000 description 5
- 239000011425 bamboo Substances 0.000 description 5
- 238000005259 measurement Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 239000000428 dust Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000012937 correction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
Images
Landscapes
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The application relates to a low-friction torque bearing set and a torque standard machine using the same, wherein the bearing set comprises a bearing seat, a rotating shaft and a force application assembly, an inner cavity is formed in the bearing seat, and the rotating shaft penetrates through the inner cavity and is rotatably connected with the bearing seat; the force application assembly is connected with the bearing seat and is used for applying radial force opposite to the direction of external radial force to the rotating shaft. This application has the effect that reduces the inside frictional force of bearing in order to promote the precision of force measuring equipment.
Description
Technical Field
The application relates to the field of bearings, in particular to a low-friction torque bearing set and a torque standard machine using the same.
Background
The bearing is an important part in the modern mechanical equipment. Its main function is to support the mechanical rotator, reduce the friction coefficient in its motion process and ensure its rotation precision.
At present, a bearing generally includes an outer ring, an inner ring, balls, a cage and a dust cap, wherein the balls are rotatably connected to the cage, the balls and the cage are disposed between the outer ring and the inner ring, and the dust cap is disposed at two sides of the cage for sealing a gap between the outer ring and the inner ring.
The bearing can also be applied to the field of force standard machines and torque standard machines, and is used as a fulcrum of the lever to realize free rotation of the lever.
With respect to the related art among the above, the inventors consider that the following drawbacks exist: the force measuring equipment such as a torque standard machine has extremely high requirements on measuring accuracy, when a lever bears large force, a bearing serving as a fulcrum can receive the action of external radial force, so that the friction force between an inner ring and an outer ring of the bearing is increased, the friction force can influence a measuring result, and the measuring accuracy is reduced.
Disclosure of Invention
In order to reduce the internal friction of the bearing and improve the precision of the force measuring device, the low-friction torque bearing set is provided.
The application provides a low friction torque bearing group adopts following technical scheme:
a low-friction torque bearing set comprises a bearing seat, a rotating shaft and a force application assembly, wherein an inner cavity is formed in the bearing seat, and the rotating shaft penetrates through the inner cavity and is rotatably connected with the bearing seat;
the force application assembly is connected with the bearing seat and used for applying radial force to the rotating shaft, wherein the direction of the radial force is opposite to that of the external radial force applied to the rotating shaft.
By adopting the technical scheme, the force application assembly applies the radial force opposite to the direction of the external radial force applied to the rotating shaft, and the external radial force applied to the rotating shaft is offset, for example, the pressure applied to the rotating shaft by a lever of a torque standard machine is reduced, and the acting force of the rotating shaft on the bearing group is reduced, so that the friction force of the bearing group can be greatly reduced, and the influence on the precision of the force measuring equipment is reduced.
Preferably, a first through hole is formed in the bottom of the bearing seat, a second through hole is formed in the top of the bearing seat, the first through hole opening and the second through hole opening are respectively communicated with the bottom and the top of the rotating shaft, the force application assembly comprises a force supply source connected with the bearing seat, and the force supply source is communicated with the first through hole to pump fluid into the inner cavity.
By adopting the technical scheme, the rotating shaft is subjected to upward radial force in the bearing seat through the force application assembly, so that the relative rotation between the rotating shaft and the bearing seat is realized, and the friction force between the rotating shaft and the bearing seat can be greatly reduced and the precision influence on the force measuring equipment is reduced due to the reduction of the acting force between the rotating shaft and the bottom wall of the inner cavity.
Preferably, radial rolling bearings are arranged on two sides of the bearing seat, which are positioned at the pressure applying position of the pressure supply source, the inner ring of each radial rolling bearing is circumferentially fixed with the rotating shaft and is in precise fit with the rotating shaft, and the outer ring of each radial rolling bearing is circumferentially fixed with the bearing seat and is in precise fit with the bearing seat.
Through adopting above-mentioned technical scheme, radial rolling bearing is used for bearing the supply pressure source to the radial force that the pivot produced and the unbalanced micro-radial force that produces of outside radial force that the pivot received, plays the guide effect to the pivot simultaneously, prevents the pivot runout.
Preferably, still include a pressure section of thick bamboo, a pressure section of thick bamboo is worn to locate in the bearing frame and with the bearing frame tight fit, third through-hole and fourth through-hole have been seted up on the pressure section of thick bamboo, the third through-hole just to the intercommunication with first through-hole and fourth through-hole just to the intercommunication with the second through-hole, pressure section of thick bamboo outer lane both ends all are equipped with the second sealing washer, the contact of second sealing washer and inner chamber inner wall, the inner wall of a pressure section of thick bamboo and the external diameter clearance fit of the bearing area of pivot.
Through adopting above-mentioned technical scheme, reduce the loss of the fluid of supplying the output of pressure source through the pressure cylinder, bear the radial force of pivot simultaneously, the second sealing washer is used for further promoting the leakproofness.
Preferably, still include the end cover, the end cover lid is located on the inner chamber opening, and its internal diameter is in order to be used for clearance seal with radial antifriction bearing's shaft shoulder clearance fit, the tang external diameter and the inner chamber of end cover closely cooperate, be provided with first sealing washer in order to realize the sealed of inner chamber between end cover and the inner chamber inner wall, end cover passes through the bolt fastening with the bearing frame.
Through adopting above-mentioned technical scheme, realize the closure of inner chamber through the end cover, realize the sealed to the clearance through first sealing washer, reduce fluidic leakage, reduce the load of pressure supply source.
Preferably, an upper cavity and a lower cavity are respectively formed at the top and the bottom of the inner wall of the pressure cylinder, the upper cavity and the lower cavity are both semicircular, the centers of the contours of the upper cavity and the lower cavity are not overlapped, the center of the contour of the lower cavity is concentric with the rotating shaft, and the inner wall of the lower cavity is in clearance fit with the outer diameter of the pressure bearing area of the rotating shaft so as to generate high fluid pressure; the outer diameter clearance fit of the upper chamber inner wall and the pressure-bearing area of the rotating shaft is used for releasing pressure of fluid of the pressure supply source, and the upper chamber inner wall is located right opposite to the direction of radial acting force of the force application assembly on the rotating shaft.
Through adopting above-mentioned technical scheme, through the pressure cylinder inner space structure of decentraction for the pivot bottom is reserved and is supplied fluid evenly distributed's clearance, makes the fluid produce the radial force that makes progress of homogeneous to the pivot, forms stable pressure and supports, with this frictional force that reduces pivot and pressure cylinder inner wall, and the clearance width at pressure cylinder top is greater than the clearance of its bottom, then can accelerate the pressure release at pivot top, forms bigger pressure differential.
Preferably, the friction torque of the radial force generated by the pressure supply source on the rotating shaft is: m = mu (F-Fx) d/2, the Fx is a radial force generated by the pressure supply source to the rotating shaft, mu is a friction coefficient, F is an external radial force applied to the rotating shaft, and d is a nominal inner diameter of the bearing.
Through adopting above-mentioned technical scheme, conventional radial antifriction bearing rotation support, its friction torque is: m = μ Fd/2, and the friction torque of the radial force generated by the pressure source on the shaft is: m = mu (F-Fx) d/2, when F-Fx =0, the friction torque is 0, the friction torque of the bearing group can be adjusted through the control of the pressure supply source, and the higher the control precision of the pressure supply source is, the smaller the adjustment error of the friction force of the bearing group is.
Preferably, the application of force subassembly includes first magnet and second magnet, first magnet with the bearing frame is connected, the second magnet is cylindric and coaxial cover is located in the pivot, the interior round polarity and the excircle polarity of second magnet are opposite, first magnet leans on the polarity of second magnet side and keeps away from the polarity opposite of second magnet side, just first magnet is located in order to exert the magnetic field force opposite with the outside radial force direction that the pivot receives to the countershaft in one side of second magnet.
By adopting the technical scheme, the repulsive force or attractive force of the first magnet and the second magnet can be converted into radial force on the rotating shaft, so that the external radial force of the rotating shaft can be counteracted, and the rotating resistance of the rotating shaft is reduced.
Preferably, the first magnet is an electromagnet or a permanent magnet, and the second magnet is a permanent magnet.
Through adopting above-mentioned technical scheme, when first magnet adopted the electro-magnet, the staff can adjust the magnetic field intensity of first magnet to this adjustment and the magnetic field force of second magnet, when the outside radial force that the pivot receives changed, adjustable magnetic field force is in order just to offset outside radial force, thereby promotes the suitability.
In a second aspect, in order to improve the measurement accuracy of the torque standard machine, the application provides a torque standard machine, which adopts the following technical scheme:
a torque standard machine comprises the low-friction torque bearing set.
Through adopting above-mentioned technical scheme, frame and the lever of moment of torsion standard machine are connected respectively to pivot and bearing frame to this reduces the atress influence to the lever through low friction moment bearing group, makes lever both sides atress balanced when rotating, thereby promotes the measurement accuracy of moment of torsion standard machine.
In summary, the present application includes at least one of the following beneficial technical effects:
1. the rotating shaft is subjected to upward radial force in the bearing seat through the pressure supply source, so that relative rotation between the rotating shaft and the bearing seat is realized, and the friction force between the rotating shaft and the bearing seat can be greatly reduced due to the reduction of the acting force between the rotating shaft and the bottom wall of the inner cavity, so that the precision influence on the force measuring equipment is reduced;
2. the radial rolling bearing is used for bearing a micro radial force generated by unbalance between a radial force generated by the pressure supply source to the rotating shaft and an external radial force received by the rotating shaft, and simultaneously plays a role in guiding the rotating shaft to prevent the rotating shaft from jumping radially;
3. the inner cavity is closed through the sealing end cover, the gap is sealed through the first sealing ring, the leakage of fluid is reduced, and the load of a pressure supply source is reduced.
Drawings
Fig. 1 is a schematic view of the overall structure of a low-friction torque bearing assembly according to embodiment 1 of the present application.
Fig. 2 is a schematic diagram of an exploded structure of the low friction torque bearing assembly of embodiment 1 of the present application, mainly showing a pressure cylinder.
Fig. 3 is a partially enlarged schematic view of a portion a in fig. 2.
Fig. 4 is a schematic cross-sectional view of the low friction torque bearing set according to embodiment 1 of the present application, taken along the radial direction of the rotating shaft.
Fig. 5 is a schematic sectional view of the low friction torque bearing set according to embodiment 1 of the present application, mainly showing a radial rolling bearing.
Fig. 6 is a schematic cross-sectional view of the low friction torque bearing set according to embodiment 2 of the present application, taken along the axial direction of the rotating shaft.
Description of reference numerals: 1. a bearing seat; 11. an inner cavity; 12. a first through hole; 13. a second through hole; 14. a radial rolling bearing; 15. a first seal ring; 16. sealing the end cap; 161. an annular groove; 2. a pressure cylinder; 21. a second seal ring; 22. a rotating shaft; 23. a third through hole; 24. a fourth via hole; 3. a force application assembly; 31. an upper chamber; 32. a lower chamber; 33. a first magnet; 34. a second magnet.
Detailed Description
The present application is described in further detail below with reference to the accompanying drawings.
Example 1:
the embodiment 1 of the application discloses a low-friction torque bearing set. Referring to fig. 1 and 2, the low friction torque bearing set includes a bearing seat 1, a pressure cylinder 2 and a force application component 3, an inner cavity 11 is provided in the bearing seat 1, the pressure cylinder 2 coaxially penetrates through the inner cavity 11 and is fixedly connected with the bearing seat 1, a rotating shaft 22 coaxially penetrates through the pressure cylinder 2, and the force application component 3 is connected with the bearing seat 1 and is used for generating a radial force which is close to and opposite to the external radial force of the rotating shaft 22 to the rotating shaft 22, so as to reduce the friction force borne by the rotating shaft 22.
An upper chamber 31 and a lower chamber 32 are respectively formed at the top and the bottom of the inner wall of the pressure cylinder, a fourth through hole 24 and a third through hole 23 are respectively formed at the top and the bottom of the pressure cylinder 2, a first through hole 12 communicated with the lower chamber 32 through the third through hole 23 is formed at the bottom of the bearing seat 1, a second through hole 13 communicated with the upper chamber 31 through the fourth through hole 24 is formed at the top of the bearing seat 1, and the second through hole 13 is communicated with the upper chamber 31 and the outside. Two sealing rings are arranged between the outer peripheral wall of the pressure cylinder 2 and the inner wall of the inner cavity 11 at intervals, the two sealing rings are positioned on two sides of the third through hole 23, and the sealing rings and the pressure cylinder 2 are coaxially distributed, so that fluid leaked from the third through hole 23 and the fourth through hole 24 is reduced.
The force application assembly 3 comprises a pressure supply source connected with the first through hole 12, the pressure supply source adopts an oil pump station, the oil pump station is communicated with the first through hole 12 through a transmission pipeline, and the transmission pipeline can be connected with an opening edge at one end of the first through hole 12 through a flange. The oil pump station is communicated with the inner cavity 11 and is used for pumping oil into the lower chamber 32, so that a pressure difference is formed between the lower chamber 32 and the upper chamber 31, the rotating shaft 22 is subjected to upward radial force, and the friction force between the rotating shaft 22 and the bearing seat 1 is reduced.
The upper chamber 31 and the lower chamber 32 are both semicircular and the centers of the outlines of the two are not coincident, and the inner wall of the upper chamber 31 is positioned right opposite to the radial acting force direction of the force application component 3 on the rotating shaft 22. The circle center of the contour of the lower chamber 32 is concentric with the rotating shaft 22, the inner wall of the lower chamber is in clearance fit with the outer diameter of the pressure bearing area of the rotating shaft 22, and the inner wall of the upper chamber 31 is in clearance fit with the outer diameter of the pressure bearing area of the rotating shaft 22. The width of the gap between the inner wall of the lower chamber 32 and the rotating shaft 22 is smaller than the width of the gap between the inner wall of the upper chamber 31 and the rotating shaft 22, and the gap at the lower chamber 32 is used for generating higher fluid pressure for decompressing the fluid of the pressure supply source, so that a larger pressure difference is formed at two sides of the rotating shaft 22.
In other embodiments, there may be at least two and an even number of the first through holes 12, and if there are two, the two first through holes 12 are symmetrically distributed along the inner cavity 11 and are located at two sides of the center of the rotation shaft 22. The two first through holes 12 enable oil input by the pressure supply source to be directly shunted, even if the radial force borne by the rotating shaft 22 deviates left and right, the fluid on the two sides of the bottom of the rotating shaft 22 is kept consistent, so that the stress on the two sides of the rotating shaft 22 is balanced, the rotating shaft 22 is prevented from deflecting due to the influence of the external force of the fluid, and the measurement accuracy is improved.
Referring to fig. 1 and 3, the top of the bearing seat 1 is semicircular, the bottom of the bearing seat is square, radial rolling bearings 14 are arranged on two sides of the pressure cylinder 2 in the inner cavity 11, the radial rolling bearings 14 are ball bearings, the rotating axis direction of the radial rolling bearings is consistent with that of the rotating shaft 22, the outer rings of the radial rolling bearings 14 are tightly matched with the inner wall of the inner cavity 11, the inner rings of the radial rolling bearings are circumferentially fixed with the rotating shaft 22, the radial rolling bearings 14 are used for bearing a small amount of radial force generated by unbalance between the radial force generated by the pressure supply to the rotating shaft 22 and the external radial force received by the rotating shaft 22, and meanwhile, the radial rolling bearings play a role in guiding the rotating shaft 22 and prevent the rotating shaft 22 from generating radial run-out.
Referring to fig. 4 and 5, the openings at two sides of the inner cavity 11 are covered with circular sealing end covers 16, the sealing end covers 16 are in insertion fit with the openings of the inner cavity 11, and the sealing end covers 16 are fixed with the shell body through bolts, so that the shell body or the sealing end covers 16 which are swelled due to long-term use are convenient to replace. When the sealing end cover 16 is inserted into the opening of the inner cavity 11, one side of the sealing end cover 16 abuts against the outer ring of the radial rolling bearing 14, and the outer ring of the other side of the radial rolling bearing 14 abuts against the pressure cylinder 2. An annular groove 161 is coaxially formed in the inner wall of the sealing end cover 16, a sealing ring is embedded in the annular groove 161, and when the sealing end cover 16 is inserted into the opening of the inner cavity 11, the sealing ring is tightly abutted against the inner wall of the inner cavity 11, so that sealing is achieved, and oil overflow is reduced.
The conventional radial rolling bearing is rotatably supported, and the friction torque is as follows: m = μ Fd/2, and the friction torque of the radial force generated by the pressure supply 6 on the shaft 2 is: m = mu (F-Fx) d/2, when F-Fx =0, the friction torque is 0, the friction torque of the bearing group can be adjusted through controlling the pressure supply source 6, and the higher the control precision of the pressure supply source 6 is, the smaller the friction force adjustment error of the bearing group is.
The specific scheme for controlling the pressure supply source 6 is as follows:
s1: calculating the weight G of the rotating shaft and the external radial force F;
s2: calculating the oil supply pressure p of the pressure supply source according to the pressure-bearing sectional area S of the pressure cylinder 2, wherein the calculation formula is p = (G + F)/S;
s3: the pressure of the pressure supply source 3 is adjusted to p.
The implementation principle of the embodiment 1 is as follows: when the bearing is started, oil is injected into the lower chamber 32 through the first through hole 12 by the pressure supply source, then the oil enters the upper chamber 31 and is discharged, so that the hydraulic pressure in the lower chamber 32 is greater than that of the upper chamber 31, the rotating shaft 22 is subjected to upward radial force, and the external radial force applied to the rotating shaft 22 is offset, for example, the pressure applied to the rotating shaft 22 by a lever of a torque standard machine is reduced, so that the friction force of the rotating shaft 22 in a bearing set is greatly reduced, the influence on the precision of force measuring equipment is reduced, meanwhile, the abrasion phenomenon is reduced, and the service life of the bearing is prolonged.
Example 2:
referring to fig. 6, a low friction torque bearing set, which is different from embodiment 1 in that: the magnetic force pushing replaces the fluid impact force and the hydraulic driving, wherein the force application component 3 comprises a first magnet 33 and a second magnet 34, the first magnet 33 is arc-shaped, the radian of the first magnet is less than 180 degrees, and the concave arc side of the first magnet faces the second magnet 34. The first magnet 33 can also be formed by uniformly distributing a plurality of magnets along the stress line of the external radial force center, and the action surface after uniform distribution does not exceed 180 radians. The first magnet 33 is positioned in a groove at the bottom of the pressure cylinder 2, the first magnet 33 is fixedly bonded with the pressure cylinder 2, and the groove is communicated with the lower chamber 32.
The first magnet 33 is located below the rotating shaft 22, the second magnet 34 is cylindrical or semi-cylindrical, the outer circular surface of the second magnet is of the same polarity, the inner circular surface of the second magnet is of the other polarity, and the second magnet is sleeved on the outer peripheral wall of the rotating shaft 22 and fixed by bolts, and the second magnet 34 can be in an integral ring shape and fixedly sleeved on the rotating shaft 22 and fastened with the outer peripheral wall of the rotating shaft 22. The first magnet 33 may be an electromagnet or a permanent magnet, and the second magnet 34 may be a permanent magnet. The polarities of the first magnet 33 and the second magnet 34 can be adjusted according to the position of the first magnet 33, as follows:
when the first magnet 33 is positioned on the top of the pressure cylinder 2, the opposite faces of the first magnet 33 and the second magnet 34 are opposite in polarity;
when the first magnet 33 is located at the bottom of the pressure cylinder 2, the opposite faces of the first magnet 33 and the second magnet 34 have the same polarity.
Taking fig. 6 as an example, the top surface of the first magnet 33 is an N pole, the bottom surface is an S pole, the second magnet 34 in the figure is cylindrical, the inner ring of the second magnet 34 is an S pole, and the outer ring is an N pole. If the second magnet 34 is a semi-cylinder, the concave arc faces upward, and the concave arc faces are S poles, while the convex arc faces close to the first magnet 33 are N poles.
If the first magnet 33 is an electromagnet, when the external radial force of the rotating shaft 22 is reduced, the electromagnet is controlled to reduce the magnetic field strength, so as to reduce the magnetic field force, and thus the upward radial force and the downward radial force applied to the rotating shaft 22 are exactly offset with each other. When the external radial force of the rotating shaft 22 is increased, the electromagnet is controlled to increase the magnetic field strength, so that the magnetic field force is increased, and the upward radial force and the downward radial force applied to the rotating shaft 22 are just counteracted with each other.
The implementation principle of the embodiment 2 is as follows: the radial force applied to the rotating shaft 22 is controlled by the repulsive force or attractive force of the magnetic field between the first magnet 33 and the second magnet 34, so that the friction force between the rotating shaft 22 and the inner wall of the pressure cylinder 2 is greatly reduced, and the influence on the accuracy of the force measuring equipment is reduced.
Example 3:
a torque standard machine is used for measuring a torque sensor and the like, and the torque sensor is taken as an example below. The torque standard machine comprises a rack, a lever and the low-friction torque bearing set, a bearing seat 1 is fixed with a rack bolt, the center of the lever is rigidly connected with two ends of a rotating shaft 22, the center of the lever is simultaneously connected with a torque sensor through a coupler, the torque sensor provides torque through a speed reduction motor and the like, and a weight is hung on the lever to detect the torque applied to the lever and check whether the torque is consistent with the reading of the torque sensor, so that the test or correction of the torque sensor is realized. The low-friction torque bearing group realizes the rotary connection of the lever and the rack, greatly reduces the stress influence on the lever, keeps the balance at the two ends of the lever and improves the measurement precision of the torque standard machine.
The above embodiments are preferred embodiments of the present application, and the protection scope of the present application is not limited by the above embodiments, so: all equivalent changes made according to the structure, shape and principle of the present application shall be covered by the protection scope of the present application.
Claims (10)
1. A low friction torque bearing pack characterized by: the bearing seat comprises a bearing seat (1), a rotating shaft (22) and a force application assembly (3), wherein an inner cavity (11) is formed in the bearing seat (1), and the rotating shaft (22) penetrates through the inner cavity (11) and is rotatably connected with the bearing seat (1);
the force application assembly (3) is connected with the bearing seat (1) and is used for applying radial force, opposite to the direction of external radial force applied to the rotating shaft (22), to the rotating shaft (22).
2. The low friction torque bearing assembly according to claim 1, wherein: first through-hole (12) have been seted up to the bottom of bearing frame (1), second through-hole (13) have been seted up at the top of bearing frame (1), first through-hole (12) opening, second through-hole (13) opening respectively with the bottom and the top intercommunication of pivot (22), application of force subassembly (3) are including the pressure supply source of being connected with bearing frame (1), pressure supply source and first through-hole (12) intercommunication are in order to pump fluid pump inner chamber (11).
3. The low friction torque bearing assembly according to claim 2, wherein: radial rolling bearings (14) are arranged on two sides of the pressure applying position of the pressure supply source on the bearing seat (1), the inner ring of each radial rolling bearing (14) is circumferentially fixed with the rotating shaft (22) and is in precise fit with the rotating shaft, and the outer ring of each radial rolling bearing is circumferentially fixed with the bearing seat (1) and is in precise fit with the rotating shaft.
4. The low friction torque bearing assembly according to claim 3, wherein: still include pressure tube (2), pressure tube (2) wear to locate in bearing frame (1) and with bearing frame (1) tight fit, third through-hole (23) and fourth through-hole (24) have been seted up on pressure tube (2), third through-hole (23) and first through-hole (12) just to intercommunication and fourth through-hole (24) just to the intercommunication with second through-hole (13), pressure tube (2) outer lane both ends all are overlapped and are equipped with second sealing washer (21), second sealing washer (21) and inner chamber (11) inner wall contact, the inner wall of pressure tube (2) and the external diameter clearance fit of the bearing area of pivot (22).
5. The low friction torque bearing assembly according to claim 4, wherein: still include end cover (16), on inner chamber (11) opening was located to end cover (16) lid, its internal diameter and the shaft shoulder clearance fit of radial antifriction bearing (14) were in order to be used for clearance seal, the tang external diameter and the inner chamber (11) of end cover (16) closely cooperate, be provided with first sealing washer (15) between end cover (16) and inner chamber (11) inner wall in order to realize the sealed of inner chamber (11), end cover (16) pass through the bolt fastening with bearing frame (1).
6. The low friction torque bearing assembly according to claim 4, wherein: an upper chamber (31) and a lower chamber (32) are respectively formed at the top and the bottom of the inner wall of the pressure cylinder (2), the upper chamber (31) and the lower chamber (32) are both semicircular, the centers of the contours of the upper chamber and the lower chamber are not overlapped, the center of the contour of the lower chamber (32) is concentric with the rotating shaft (22), and the inner wall of the lower chamber is in clearance fit with the outer diameter of a pressure bearing area of the rotating shaft (22) so as to generate high fluid pressure; go up cavity (31) inner wall and the external diameter clearance fit of the pressure-bearing area of pivot (22) in order to be used for the fluid pressure release to the pressure supply source, go up cavity (31) inner wall and be located application of force subassembly (3) right opposite to pivot (22) radial effort direction.
7. The low friction torque bearing assembly according to claim 2, wherein: the friction torque of the radial force generated by the pressure supply source on the rotating shaft (2) is as follows: m = mu (F-Fx) d/2, the Fx is a radial force generated by the pressure supply source to the rotating shaft (2), mu is a friction coefficient, F is an external radial force applied to the rotating shaft, and d is a nominal inner diameter of the bearing.
8. The low friction torque bearing assembly according to claim 1, wherein: force application component (3) include first magnet (33) and second magnet (34), first magnet (33) with bearing frame (1) is connected, second magnet (34) are cylindric and coaxial cover and locate on pivot (22), the interior circular polarity and the excircle polarity of second magnet (34) are opposite, first magnet (33) lean on the polarity of second magnet (34) side and keep away from the polarity of second magnet (34) side opposite, just first magnet (33) are located one side of second magnet (34) is in order to exert the magnetic field force that receives with pivot (22) outside radial force opposite direction to countershaft (22).
9. The low friction torque bearing assembly according to claim 8, wherein: the first magnet (33) adopts an electromagnet or a permanent magnet, and the second magnet (34) adopts a permanent magnet.
10. A torque standard machine comprising a low friction torque bearing pack according to any one of claims 1 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111638060.2A CN114321188B (en) | 2021-12-29 | 2021-12-29 | Low friction moment bearing group and torque standard machine applying same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111638060.2A CN114321188B (en) | 2021-12-29 | 2021-12-29 | Low friction moment bearing group and torque standard machine applying same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114321188A true CN114321188A (en) | 2022-04-12 |
| CN114321188B CN114321188B (en) | 2024-05-14 |
Family
ID=81017808
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111638060.2A Active CN114321188B (en) | 2021-12-29 | 2021-12-29 | Low friction moment bearing group and torque standard machine applying same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114321188B (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1330317A (en) * | 1969-10-10 | 1973-09-19 | Anvar | Method of centering a shaft in a bearing and hydrostatic bearing with high rigidity for carrying out this method |
| JPS61170628A (en) * | 1985-01-25 | 1986-08-01 | Toyota Motor Corp | Bearing torque measuring instrument |
| JPH0681838A (en) * | 1992-08-29 | 1994-03-22 | Teijin Seiki Co Ltd | Hybrid air bearing |
| JPH06311702A (en) * | 1993-04-19 | 1994-11-04 | Koyo Seiko Co Ltd | Spindle motor |
| WO2001084693A1 (en) * | 2000-05-01 | 2001-11-08 | Indigo Energy, Inc. | Full levitation bearing system with improved passive radial magnetic bearings |
| JP2005240978A (en) * | 2004-02-27 | 2005-09-08 | Mitsubishi Heavy Ind Ltd | Rolling bearing mechanism and electric equipment using it |
| CN205446397U (en) * | 2016-01-06 | 2016-08-10 | 上海大学 | Antifriction bearing with radial permanent magnetism suspension additional bearing |
| CN106197843A (en) * | 2016-08-31 | 2016-12-07 | 北京航天动力研究所 | A kind of on-site torsion calibration device |
| US20170268524A1 (en) * | 2015-02-24 | 2017-09-21 | Nidec Copal Electronics Corporation | Motor, and motor control system |
| WO2020013276A1 (en) * | 2018-07-11 | 2020-01-16 | 日本精工株式会社 | Bearing device and machine tool spindle apparatus |
| WO2020059935A1 (en) * | 2018-09-20 | 2020-03-26 | 한국생산기술연구원 | Composite bearing, and power generator and power generation system including same |
| US20200149992A1 (en) * | 2017-05-17 | 2020-05-14 | Zf Friedrichshafen Ag | Test bench arrangement for testing a multi-plate clutch |
-
2021
- 2021-12-29 CN CN202111638060.2A patent/CN114321188B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1330317A (en) * | 1969-10-10 | 1973-09-19 | Anvar | Method of centering a shaft in a bearing and hydrostatic bearing with high rigidity for carrying out this method |
| JPS61170628A (en) * | 1985-01-25 | 1986-08-01 | Toyota Motor Corp | Bearing torque measuring instrument |
| JPH0681838A (en) * | 1992-08-29 | 1994-03-22 | Teijin Seiki Co Ltd | Hybrid air bearing |
| JPH06311702A (en) * | 1993-04-19 | 1994-11-04 | Koyo Seiko Co Ltd | Spindle motor |
| WO2001084693A1 (en) * | 2000-05-01 | 2001-11-08 | Indigo Energy, Inc. | Full levitation bearing system with improved passive radial magnetic bearings |
| JP2005240978A (en) * | 2004-02-27 | 2005-09-08 | Mitsubishi Heavy Ind Ltd | Rolling bearing mechanism and electric equipment using it |
| US20170268524A1 (en) * | 2015-02-24 | 2017-09-21 | Nidec Copal Electronics Corporation | Motor, and motor control system |
| CN205446397U (en) * | 2016-01-06 | 2016-08-10 | 上海大学 | Antifriction bearing with radial permanent magnetism suspension additional bearing |
| CN106197843A (en) * | 2016-08-31 | 2016-12-07 | 北京航天动力研究所 | A kind of on-site torsion calibration device |
| US20200149992A1 (en) * | 2017-05-17 | 2020-05-14 | Zf Friedrichshafen Ag | Test bench arrangement for testing a multi-plate clutch |
| WO2020013276A1 (en) * | 2018-07-11 | 2020-01-16 | 日本精工株式会社 | Bearing device and machine tool spindle apparatus |
| WO2020059935A1 (en) * | 2018-09-20 | 2020-03-26 | 한국생산기술연구원 | Composite bearing, and power generator and power generation system including same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114321188B (en) | 2024-05-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5297190B2 (en) | Vacuum pump | |
| US6176618B1 (en) | Dynamic pressure bearing, spindle motor using dynamic pressure bearing, and rotary device having the spindle motor as driving source | |
| US6081057A (en) | Spindel motor for a disc drive | |
| CN107100930B (en) | A kind of electromagnetism-static pressure dual suspension thrust bearing | |
| JP2001527478A (en) | 4-ring eccentric bearing for printing press cylinder | |
| KR20060114883A (en) | A hydrodynamic bearing motor uing a fixed shaft | |
| CA2052475C (en) | Rotary-anode type x-ray tube | |
| JP2016161117A (en) | Cycloid speed reducer and motor drive device with cycloid speed reducer | |
| CN114321188A (en) | Low friction torque bearing set and torque standard machine applying same | |
| JPS6018930B2 (en) | Centering and holding device for a rotating body in a hanging test machine | |
| CN106870557A (en) | Rolling bearing, concussion system and rotary system for root of blade | |
| US4167845A (en) | Axial guide for the shaft of a spinning rotor | |
| CN108775334A (en) | High-accuracy magnetic-suspension main-shaft | |
| CN203730561U (en) | Aerostatic bearing | |
| US2676853A (en) | Bearing mounting | |
| KR20130107506A (en) | Fluid hydrodynamic bearing and spindle motor having the same | |
| JP2004190855A (en) | Spindle motor | |
| CN111623038B (en) | Ultra-high precision hydrostatic bearing | |
| CN101924413A (en) | Permanent magnet and rolling-sliding bearing type motor rotor bearing and rotary machine with same | |
| EP0794344A4 (en) | High-speed rotary body | |
| US3913991A (en) | Lower bearing for rotors which revolve at high speeds and have an essentially vertical axis of rotation | |
| RU2205309C2 (en) | Magnetic fluid seal | |
| CN110307340A (en) | A kind of mechanically-sealing apparatus of high speed and high pressure hydraulic pump | |
| CN214789635U (en) | High-rotating-speed rotary joint | |
| KR20030090561A (en) | Fluid dynamic bearing spindle motor |
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 |