CN114321188B - Low friction moment bearing group and torque standard machine applying same - Google Patents
Low friction moment bearing group and torque standard machine applying same Download PDFInfo
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- CN114321188B CN114321188B CN202111638060.2A CN202111638060A CN114321188B CN 114321188 B CN114321188 B CN 114321188B CN 202111638060 A CN202111638060 A CN 202111638060A CN 114321188 B CN114321188 B CN 114321188B
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- 238000007789 sealing Methods 0.000 claims description 42
- 238000005096 rolling process Methods 0.000 claims description 22
- 239000012530 fluid Substances 0.000 claims description 16
- 230000000149 penetrating effect Effects 0.000 claims description 3
- BJQHLKABXJIVAM-UHFFFAOYSA-N bis(2-ethylhexyl) phthalate Chemical compound CCCCC(CC)COC(=O)C1=CC=CC=C1C(=O)OCC(CC)CCCC BJQHLKABXJIVAM-UHFFFAOYSA-N 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 2
- 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
- 230000001174 ascending effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007774 longterm Effects 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
- 238000009827 uniform distribution Methods 0.000 description 1
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Abstract
The application relates to a low friction moment bearing group and a torque standard machine using the same, wherein the bearing group comprises a bearing seat, a rotating shaft and a force application component, an inner cavity is formed in the bearing seat, and the rotating shaft penetrates through the inner cavity and is in rotating connection with the bearing seat; the force application component is connected with the bearing seat and is used for applying radial force opposite to the external radial force to the rotating shaft. The application has the effect of reducing the friction force in the bearing so as to improve the precision of the force measuring equipment.
Description
Technical Field
The application relates to the field of bearings, in particular to a low friction moment bearing set and a torque standard machine using the same.
Background
Bearings are an important component in contemporary mechanical devices. Its main function is to support the mechanical rotator, reduce the friction coefficient in the course of its movement and ensure its rotation accuracy.
At present, the bearing generally comprises an outer ring, an inner ring, balls, a retainer and a dust cover, wherein the balls are rotationally connected to the retainer, the balls and the retainer are placed between the outer ring and the inner ring, and the dust cover is positioned on two sides of the retainer and used for sealing a gap between the outer ring and the inner ring.
The bearing can also be applied to the fields 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 described above, the inventors consider that there are the following drawbacks: the requirements of force measuring equipment such as a torque standard machine and the like on measuring precision are extremely high, when a lever bears larger force, a bearing serving as a fulcrum can receive external radial force, so that 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 precision is reduced.
Disclosure of Invention
In a first aspect, the present application provides a low friction torque bearing assembly for reducing friction within a bearing and improving accuracy of a force measuring device.
The application provides a low friction moment bearing group, which adopts the following technical scheme:
The bearing block comprises a bearing block, a rotating shaft and a force application component, wherein an inner cavity is formed in the bearing block, and the rotating shaft penetrates through the inner cavity and is in rotary connection with the bearing block;
the force application component is connected with the bearing seat and is used for applying radial force to the rotating shaft, wherein the radial force is opposite to the direction of external radial force applied to the rotating shaft.
By adopting the technical scheme, the external radial force applied to the rotating shaft is counteracted by the force application component, wherein the direction of the radial force is opposite to the direction of the external radial force applied to the rotating shaft, for example, the pressure applied to the rotating shaft by the lever of the torque standard machine is counteracted.
Preferably, the bottom of bearing frame has seted up first through-hole, the second through-hole has been seted up at the top of bearing frame, first through-hole opening, second through-hole opening respectively with the bottom and the top intercommunication of pivot, the application of force subassembly includes the pressure supply source of being connected with the bearing frame, pressure supply source and first through-hole intercommunication are in order to pump into the inner chamber with fluid.
Through adopting above-mentioned technical scheme, make the pivot receive ascending radial force in the bearing frame through the application of force subassembly to this relative rotation between realization pivot and the bearing frame, because the effort between pivot and the inner chamber diapire reduces, with this frictional force between can reduce by a wide margin pivot and the bearing frame, reduce the precision influence to force measuring equipment.
Preferably, radial rolling bearings are arranged on the bearing seat at two sides of the pressing part of the pressure supply source, an inner ring of each radial rolling bearing is fixed with the rotating shaft in the circumferential direction and is in precise fit with the rotating shaft, and an outer ring of each radial rolling bearing is fixed with the bearing seat in the circumferential direction and is in precise fit with the bearing seat.
By adopting the technical scheme, the radial rolling bearing is used for bearing the micro radial force generated by unbalanced radial force of the pressure supply source on the rotating shaft and the external radial force born by the rotating shaft, and plays a guiding role on the rotating shaft at the same time, so that the radial runout of the rotating shaft is prevented.
Preferably, the novel bearing further comprises a pressure cylinder, wherein the pressure cylinder penetrates through the bearing seat and is in tight fit with the bearing seat, a third through hole and a fourth through hole are formed in the pressure cylinder, the third through hole is directly opposite to the first through hole and is directly opposite to the second through hole, second sealing rings are respectively sleeved at two ends of an outer ring of the pressure cylinder, the second sealing rings are in contact with the inner wall of an inner cavity, and the inner wall of the pressure cylinder is in clearance fit with the outer diameter of a bearing area of the rotating shaft.
Through adopting above-mentioned technical scheme, reduce the loss of the fluid that supplies the pressure source output through the pressure tube, bear the radial force of pivot simultaneously, the second sealing washer is used for further promoting the leakproofness.
Preferably, the sealing device further comprises a sealing end cover, wherein the sealing end cover is covered on the inner cavity opening, the inner diameter of the sealing end cover is in clearance fit with the shaft shoulder of the radial rolling bearing for clearance sealing, the outer diameter of the spigot of the sealing end cover is in tight fit with the inner cavity, a first sealing ring is arranged between the sealing end cover and the inner wall of the inner cavity to seal the inner cavity, and the sealing end cover is fixed with the bearing seat through bolts.
Through adopting above-mentioned technical scheme, realize the closure of inner chamber through the seal end cover, realize the seal to the clearance through first sealing washer, reduce the leakage of fluid, reduce the load of supply pressure source.
Preferably, an upper chamber and a lower chamber are respectively formed at the top and the bottom of the inner wall of the pressure cylinder, the upper chamber and the lower chamber are semicircular, the circle centers of the outlines of the upper chamber and the lower chamber are not coincident, the circle center of the outline of the lower chamber is concentric with the rotating shaft, and the inner wall of the lower chamber is in clearance fit with the outer diameter of the bearing area of the rotating shaft so as to generate high fluid pressure; the inner wall of the upper chamber is in clearance fit with the outer diameter of the bearing area of the rotating shaft so as to be used for releasing pressure of fluid of a pressure supply source, and the inner wall of the upper chamber is positioned 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 inside space structure of the pressure cylinder of non-concentricity for the clearance that supplies fluid evenly distributed is reserved to the pivot bottom, makes the fluid produce even radial force that makes progress to the pivot, forms stable pressure support, 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 moment of the radial force generated by the pressure supply source on the rotating shaft is: m=μ (F-Fx) d/2, fx is the radial force generated by the pressure supply source on the rotating shaft, μ is the friction coefficient, F is the external radial force received by the rotating shaft, and d is the nominal inner diameter of the bearing.
By adopting the technical scheme, the conventional radial rolling bearing is rotatably supported, and the friction moment is as follows: m=μfd/2, and the friction torque of the radial force generated by the pressure supply source on the rotating shaft is: m=mu (F-Fx) d/2, and when F-fx=0, the friction moment is 0, and the friction moment of the bearing group can be adjusted through controlling the pressure supply source, so that the higher the control precision of the pressure supply source is, the smaller the friction force adjusting error of the bearing group is.
Preferably, the force application assembly comprises a first magnet and a second magnet, the first magnet is connected with the bearing seat, the second magnet is cylindrical and coaxially sleeved on the rotating shaft, the polarity of the inner circle of the second magnet is opposite to the polarity of the outer circle of the second magnet, the polarity of the first magnet on the side of the second magnet is opposite to the polarity of the first magnet on the side far away from the second magnet, and the first magnet is positioned on one side of the second magnet so as to apply magnetic force opposite to the direction of external radial force applied to the rotating shaft.
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 to the rotating shaft, so that the external radial force of the rotating shaft can be offset, and the rotating resistance of the rotating shaft is reduced.
Preferably, the first magnet may be an electromagnet or a permanent magnet, and the second magnet may be a permanent magnet.
Through adopting above-mentioned technical scheme, when first magnet adopts the electro-magnet, the magnetic field strength of first magnet can be adjusted to this adjustment and the magnetic field force of second magnet, when the pivot receives outside radial force to change, adjustable magnetic field force just offsets 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, pivot and bearing frame are connected frame and the lever of moment of torsion standard machine respectively to this reduces the atress influence to the lever through low friction moment bearing group, makes the 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 pressure supply source enables the rotating shaft to receive upward radial force in the bearing seat, 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 due to the fact that the acting force between the rotating shaft and the bottom wall of the inner cavity is reduced, and the influence on the precision of the force measuring equipment is reduced;
2. The radial rolling bearing is used for bearing a trace radial force generated by unbalance between the radial force generated by the pressure supply source to the rotating shaft and the external radial force applied to the rotating shaft, and plays a role in guiding the rotating shaft to prevent the radial runout of the rotating shaft;
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 showing the overall structure of a low friction torque bearing assembly according to embodiment 1 of the present application.
Fig. 2 is an exploded view of the low friction torque bearing assembly of embodiment 1 of the present application, mainly showing the pressure cylinder.
Fig. 3 is an enlarged partial schematic view of the portion a in fig. 2.
Fig. 4 is a schematic cross-sectional view of the low friction torque bearing assembly of embodiment 1 of the present application along the radial direction of the rotation 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 radial rolling bearings.
Fig. 6 is a schematic cross-sectional view of the low friction torque bearing assembly according to embodiment 2 of the present application along the axial direction of the shaft.
Reference numerals illustrate: 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 cover; 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 through hole; 3. a force application assembly; 31. an upper chamber; 32. a lower chamber; 33. a first magnet; 34. and a second magnet.
Detailed Description
The present application will be described in further detail below with reference to the accompanying drawings.
Example 1:
The embodiment 1 of the application discloses a low friction moment bearing group. Referring to fig. 1 and 2, the low friction moment bearing set includes a bearing seat 1, a pressure cylinder 2 and a force application component 3, wherein an inner cavity 11 is formed in the bearing seat 1, the pressure cylinder 2 is coaxially arranged in the inner cavity 11 in a penetrating manner and fixedly connected with the bearing seat 1, a rotating shaft 22 is coaxially arranged in the pressure cylinder 2 in a penetrating manner, and the force application component 3 is connected with the bearing seat 1 and is used for generating a radial force to the rotating shaft 22, wherein the radial force is close to the external radial force of the rotating shaft 22 and has opposite directions, so that the friction force born by the rotating shaft 22 is reduced.
The top and the bottom of the inner wall of the pressure cylinder are respectively provided with an upper chamber 31 and a lower chamber 32, the top and the bottom of the pressure cylinder 2 are respectively provided with a fourth through hole 24 and a third through hole 23, the bottom of the bearing seat 1 is provided with a first through hole 12 communicated with the lower chamber 32 through the third through hole 23, the top of the bearing seat 1 is provided with a second through hole 13 communicated with the upper chamber 31 through the fourth through hole 24, 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 at two sides of the third through hole 23, and the sealing rings and the pressure cylinder 2 are coaxially distributed, so that fluid leaking 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, wherein 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 flange at one end of the first through hole 12. The oil pump station is communicated with the inner cavity 11 and is used for pumping oil into the lower chamber 32, so that the lower chamber 32 and the upper chamber 31 form a pressure difference, 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 semicircular, the centers of the outlines of the upper chamber 31 and the lower chamber 32 are not coincident, and the inner wall of the upper chamber 31 is positioned on the right opposite side of the force application component 3 to the radial acting force direction of the rotating shaft 22. The center of the outline 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 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 bearing area of the rotating shaft 22. The gap width between the inner wall of the lower chamber 32 and the rotating shaft 22 is smaller than that 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 and releasing the pressure of 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, the number of the first through holes 12 is at least two and even, if 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 liquid input by a pressure source to be directly split, even if radial force borne by the rotating shaft 22 is offset left and right, fluid on two sides of the bottom of the rotating shaft is consistent, so that the stress on two sides of the rotating shaft 22 is balanced, deflection trend caused by the influence of external force of the fluid on the rotating shaft 22 is avoided, and further 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 rotation axis direction of the radial rolling bearings 14 is consistent with the rotation axis direction of the rotating shaft 22, the outer ring of the radial rolling bearings 14 is tightly matched with the inner wall of the inner cavity 11, the inner ring of the radial rolling bearings is circumferentially fixed with the rotating shaft 22, and the radial rolling bearings 14 are used for bearing micro radial forces generated by unbalanced radial forces generated by the pressure source on the rotating shaft 22 and external radial forces received by the rotating shaft 22, and meanwhile play a guiding role on the rotating shaft 22 to prevent the rotating shaft 22 from radial runout.
Referring to fig. 4 and 5, circular sealing end covers 16 are respectively covered on openings on two sides of the inner cavity 11, the sealing end covers 16 are in plug-in fit with the openings of the inner cavity 11, and the sealing end covers 16 are fixed with the shell through bolts, so that the shell or the sealing end covers 16 which bulge due to long-term use can be replaced conveniently. When the sealing end cover 16 is inserted into the opening of the inner cavity 11, one side of the sealing end cover 16 is abutted against the outer ring of the radial rolling bearing 14, and the outer ring of the other side of the radial rolling bearing 14 is abutted against the pressure cylinder 2. An annular groove 161 is coaxially formed in the inner wall of the sealing end cover 16, and a sealing ring is embedded in the annular groove 161, so that when the sealing end cover 16 is inserted into an opening of the inner cavity 11, the sealing ring abuts against the inner wall of the inner cavity 11, and sealing is realized, and oil overflow is reduced.
The friction moment of the conventional radial rolling bearing rotary support is as follows: m=μfd/2, and the friction torque of the radial force generated by the pressure supply source 6 on the rotating shaft 2 is: m=mu (F-Fx) d/2, and when F-fx=0, the friction torque is 0, and the friction torque of the bearing group can be adjusted by controlling the pressure supply source 6, so that 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: according to the pressure-bearing sectional area S of the pressure cylinder 2, calculating the oil supply pressure p of the pressure supply source, 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, the oil is injected into the lower chamber 32 through the first through hole 12 by the pressure supply source, and 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, the external radial force applied to the rotating shaft 22, such as the pressure applied to the rotating shaft 22 by the lever of the torque standard machine, is counteracted, the friction force of the rotating shaft 22 in the bearing group is greatly reduced, the influence on the accuracy of force measuring equipment is reduced, 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 is different from embodiment 1 in that: the force application assembly 3 comprises a first magnet 33 and a second magnet 34, wherein the first magnet 33 is in a circular arc shape, the radian of the first magnet is smaller than 180 degrees, and the concave arc side of the first magnet is towards the second magnet 34. The first magnet 33 can also be formed by uniformly distributing a plurality of magnets along the external radial force center stress line, and the action surface after uniform distribution does not exceed 180 radians. The first magnet 33 is located in a groove at the bottom of the pressure cylinder 2, and the first magnet 33 is fixedly adhered to 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, the second magnet is sleeved on the outer peripheral wall of the rotating shaft 22 and is fixed by bolts, the second magnet 34 can be in an integral ring shape, and the second magnet is fixedly sleeved on the rotating shaft 22 and is 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, specifically 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 N pole, the bottom surface is S pole, the second magnet 34 is cylindrical in the drawing, the inner ring of the second magnet 34 is S pole, and the outer ring is N pole. If the second magnet 34 is semi-cylindrical, the concave arc surface faces upward, the concave arc surface is the S pole, and the convex arc surface adjacent to the first magnet 33 is the N pole.
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 that the magnetic field force is reduced, and the rotating shaft 22 is subjected to the upward radial force and the downward radial force are exactly offset. When the external radial force of the rotating shaft 22 increases, the electromagnet is controlled to increase the magnetic field strength, so that the upward radial force and the downward radial force of the rotating shaft 22 just cancel each other.
The implementation principle of the embodiment 2 is as follows: the magnitude of 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 device is reduced.
Example 3:
A torque standard machine is used for measuring a torque sensor or the like, and the torque sensor is taken as an example. The torque standard machine comprises a frame, a lever and the low friction torque bearing group, wherein the bearing seat 1 is fixed with the frame through bolts, the center of the lever is rigidly connected with two ends of the rotating shaft 22, the center of the lever is simultaneously connected with the torque sensor through a coupler, the torque sensor provides torque through a gear motor and the like, and weights are hung on the lever to detect the torque received by the lever and detect whether the torque is consistent with the reading of the torque sensor, so that the torque sensor is tested or corrected. The rotary connection of the lever and the frame is realized through the low friction moment bearing group, the stress influence on the lever is greatly reduced, and the balance of the two ends of the lever is maintained, so that the measurement accuracy of the torque standard machine is improved.
The above embodiments are not intended to limit the scope of the present application, so: all equivalent changes in structure, shape and principle of the application should be covered in the scope of protection of the application.
Claims (7)
1. A low friction torque bearing set, characterized by: the device comprises a bearing seat (1), a rotating shaft (22) and a force application component (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 in rotary connection with the bearing seat (1);
The force application component (3) is connected with the bearing seat (1) and is used for applying radial force to the rotating shaft (22) in the direction opposite to the external radial force applied to the rotating shaft (22);
the bottom of the bearing seat (1) is provided with a first through hole (12), the top of the bearing seat (1) is provided with a second through hole (13), the openings of the first through hole (12) and the second through hole (13) are respectively communicated with the bottom and the top of the rotating shaft (22), the force application assembly (3) comprises a pressure supply source connected with the bearing seat (1), and the pressure supply source is communicated with the first through hole (12) to pump fluid into the inner cavity (11);
The novel hydraulic pressure cylinder is characterized by further comprising a pressure cylinder (2), wherein the pressure cylinder (2) is arranged in the bearing seat (1) in a penetrating manner and is in tight fit with the bearing seat (1), a third through hole (23) and a fourth through hole (24) are formed in the pressure cylinder (2), the third through hole (23) is directly opposite to the first through hole (12) to be communicated, the fourth through hole (24) is directly opposite to the second through hole (13) to be communicated, two ends of an outer ring of the pressure cylinder (2) are respectively sleeved with a second sealing ring (21), the second sealing rings (21) are in contact with the inner wall of the inner cavity (11), and the inner wall of the pressure cylinder (2) is in clearance fit with the outer diameter of a bearing area of 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 (2), the upper chamber (31) and the lower chamber (32) are semicircular, the circle centers of the outlines of the upper chamber and the lower chamber are not coincident, the circle center of the outline 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 bearing area of the rotating shaft (22) so as to generate high fluid pressure; the inner wall of the upper chamber (31) is in clearance fit with the outer diameter of the bearing area of the rotating shaft (22) so as to be used for pressure relief of fluid of a pressure supply source, and the inner wall of the upper chamber (31) is positioned right opposite to the direction of radial acting force of the force application assembly (3) on the rotating shaft (22).
2. The low friction torque bearing set according to claim 1, wherein: radial rolling bearings (14) are arranged on the bearing seat (1) and positioned on two sides of the pressing part of the pressure supply source, an 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 an outer ring of each radial rolling bearing is circumferentially fixed with the bearing seat (1) and is in precise fit with the rotating shaft.
3. The low friction torque bearing set according to claim 1, wherein: the sealing device is characterized by further comprising a sealing end cover (16), wherein the sealing end cover (16) is covered on an opening of the inner cavity (11), the inner diameter of the sealing end cover is in clearance fit with a shaft shoulder of the radial rolling bearing (14) for clearance sealing, the spigot outer diameter of the sealing end cover (16) is in tight fit with the inner cavity (11), a first sealing ring (15) is arranged between the sealing end cover (16) and the inner wall of the inner cavity (11) to seal the inner cavity (11), and the sealing end cover (16) is fixed with the bearing seat (1) through bolts.
4. The low friction torque bearing set according to claim 1, wherein: the friction moment of the radial force generated by the pressure supply source on the rotating shaft (22) is as follows: m=μ (F-Fx) d/2, fx is a radial force generated by the pressure supply source on the rotating shaft (22), μ is a friction coefficient, F is an external radial force received by the rotating shaft, and d is a nominal inner diameter of the bearing.
5. The low friction torque bearing set according to claim 1, wherein: the force application assembly (3) comprises a first magnet (33) and a second magnet (34), the first magnet (33) is connected with the bearing seat (1), the second magnet (34) is cylindrical and coaxially sleeved on the rotating shaft (22), the polarity of the inner circle of the second magnet (34) is opposite to the polarity of the outer circle, the polarity of the first magnet (33) close to the second magnet (34) is opposite to the polarity of the side far away from the second magnet (34), and the first magnet (33) is positioned on one side of the second magnet (34) so as to apply magnetic force to the rotating shaft (22) in the direction opposite to the direction of external radial force applied to the rotating shaft (22).
6. The low friction torque bearing set according to claim 5, wherein: the first magnet (33) adopts an electromagnet or a permanent magnet, and the second magnet (34) adopts a permanent magnet.
7. A torque etalon comprising the low friction torque bearing set according to any one of claims 1 to 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202111638060.2A CN114321188B (en) | 2021-12-29 | 2021-12-29 | Low friction moment bearing group and torque standard machine applying same |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111638060.2A CN114321188B (en) | 2021-12-29 | 2021-12-29 | Low friction moment bearing group and torque standard machine applying same |
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| CN114321188B true CN114321188B (en) | 2024-05-14 |
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| JP6391496B2 (en) * | 2015-02-24 | 2018-09-19 | 日本電産コパル電子株式会社 | Motor, motor control system |
| DE102017208311A1 (en) * | 2017-05-17 | 2018-11-22 | Zf Friedrichshafen Ag | Test rig arrangement for testing a multi-disc clutch |
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| CN114321188A (en) | 2022-04-12 |
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