CN113404778B - Water lubrication tail bearing device with high bearing capacity and vibration reduction - Google Patents
Water lubrication tail bearing device with high bearing capacity and vibration reduction Download PDFInfo
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- CN113404778B CN113404778B CN202110581439.8A CN202110581439A CN113404778B CN 113404778 B CN113404778 B CN 113404778B CN 202110581439 A CN202110581439 A CN 202110581439A CN 113404778 B CN113404778 B CN 113404778B
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 32
- 238000005461 lubrication Methods 0.000 title claims abstract description 18
- 230000009467 reduction Effects 0.000 title abstract description 23
- 238000013016 damping Methods 0.000 claims abstract description 48
- 238000007789 sealing Methods 0.000 claims abstract description 42
- 230000009471 action Effects 0.000 claims abstract description 9
- 230000001020 rhythmical effect Effects 0.000 claims abstract description 5
- 230000000149 penetrating effect Effects 0.000 claims abstract description 4
- 238000005520 cutting process Methods 0.000 claims description 17
- 239000000463 material Substances 0.000 claims description 13
- 238000000034 method Methods 0.000 claims description 6
- 238000010892 electric spark Methods 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 13
- 230000021715 photosynthesis, light harvesting Effects 0.000 abstract description 4
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 239000010410 layer Substances 0.000 description 14
- 238000005457 optimization Methods 0.000 description 5
- 238000009826 distribution Methods 0.000 description 4
- 238000002955 isolation Methods 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000004048 modification Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 229910000975 Carbon steel Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000010962 carbon steel Substances 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000000704 physical effect Effects 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 239000002344 surface layer Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/12—Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
- F16C33/122—Multilayer structures of sleeves, washers or liners
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/124—Elastomeric springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
- F16F15/161—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material characterised by the fluid damping devices, e.g. passages, orifices
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Support Of The Bearing (AREA)
Abstract
The invention discloses a water lubrication tail bearing device with high bearing capacity and vibration reduction, which comprises a bearing lining, a bearing bush, a sealing end cover and a damping structure, wherein the bearing lining and a bearing shaft sleeve are of a coaxial cylindrical structure, the inner wall of the bearing lining is matched with a working shaft, and the outer wall of the bearing lining is matched with the bearing bush; the outer wall of the bearing bush is connected with the base; the sealing end cover is annular and is coaxially arranged at the end part of the bearing bush, a notch is formed in the inner side wall of the sealing end cover, a sealing oil cavity is formed between the notch and the end face of the bearing bush, and oil is filled in the sealing oil cavity; the damping structure is a clearance structure penetrating through two end faces of the bearing bush. The beneficial effects of the invention are as follows: the damping structure is additionally arranged in the bearing bush, the damping structure can generate rhythmic stretching deformation under the action of exciting force, oil is sucked and discharged in the gap along the axial direction to generate a piston effect, and larger damping is generated so as to form energy dissipation, so that the purpose of reducing shafting vibration is achieved.
Description
Technical Field
The invention relates to the technical field of water lubrication tail bearings, in particular to a water lubrication tail bearing device with high bearing capacity and vibration reduction.
Background
The stern bearing is a key component of the propulsion shafting and is used for bearing the weight of the propeller and the transmission shaft. The water lubrication tail bearing is used as a first link for transmitting shafting vibration to a foundation and even a ship body, and the vibration reduction performance of the water lubrication tail bearing plays an important role in controlling shafting vibration. The water lubrication bearing has severe working conditions, and because the interface is in a mixed lubrication state, local contact friction and abrasion are easy to occur, and abnormal noise and shaft vibration are generated.
The traditional water lubrication tail bearing consists of a lining and a lining, wherein the lining is made of copper or stainless steel, and the lining is made of polymer composite materials such as rubber (NBR), sialon (Thorton), feroform and the like. At present, the optimization of the lining structure and the material modification are two common optimization methods aiming at the vibration reduction problem of the water lubrication tail bearing. In the aspect of optimizing the lining structure, the lubricating performance of the bearing can be improved by optimizing the geometrical parameters of the surface layer of the bushing, the geometrical parameters of the water tank or designing the surface structure, so that the shafting vibration is indirectly reduced; the modification of the lining material is to add a small amount of modifying elements or components on the basis of the existing lining material, so as to improve the bearing performance. However, the optimization methods are difficult to meet the requirements of bearing capacity and vibration reduction capacity, and mainly because the bearing lining layer bears the requirements of bearing capacity and vibration reduction function, but under severe working conditions such as unbalanced load and heavy load, the soft lining layer can generate obvious extrusion deformation, and the optimization methods such as lining optimization and micro-texture are often compacted to greatly weaken the damping effect, so that the contradiction of bearing capacity and vibration reduction is difficult to be well reconciled by simply optimizing the physical properties of the lining.
From a vibration isolation perspective, the bearing liner serves to isolate vibration and desirably transfer as little vibration energy from the shaft to the bearing housing as possible. According to the linear vibration isolation theory, only when the excitation frequency is greater thanWhen the natural frequency of the vibration isolation system is multiplied, the system has vibration isolation effect. Therefore, the natural frequency of the bearing liner should be minimized without changing the excitation frequency. However, in order to increase the load carrying capacity of the bearing, a relatively high stiffness of the bearing is required, but a high stiffness tends to result in a relatively high natural frequency. Therefore, the contradiction between high carrying capacity and low natural frequency becomes one of the bottlenecks in the development of the ship water-lubricated tail bearing vibration reduction technology.
Disclosure of Invention
The invention aims to provide a water lubrication tail bearing device with high bearing capacity and vibration reduction, which solves the problem that the existing ship water lubrication tail shaft has contradictory high bearing capacity and low natural frequency.
The invention adopts the technical scheme that: the water lubrication tail bearing device with high bearing capacity and vibration reduction comprises a bearing lining, a bearing bush, a sealing end cover and a damping structure, wherein the bearing lining and a bearing shaft sleeve are of a coaxial cylindrical structure, the inner wall of the bearing lining is matched with a working shaft, and the outer wall of the bearing lining is matched with the bearing bush; the outer wall of the bearing bush is connected with the base; the sealing end cover is annular and is coaxially arranged at the end part of the bearing bush, a notch is formed in the inner side wall of the sealing end cover, a sealing oil cavity is formed between the notch and the end face of the bearing bush, and oil is filled in the sealing oil cavity; the damping structure is a clearance structure penetrating through two end surfaces of the bearing bush, and the clearance structure is respectively communicated with the sealing oil cavities at two ends; when vibration is generated, the oil in the sealed oil cavity is axially sucked and discharged in the gap structure through the stretching deformation of the gap structure.
According to the scheme, the gap structure comprises at least two layers of intermittent kerfs which are annularly cut on the bearing bush, and the diameters of the intermittent kerfs are different; the radial overlapping parts of the intermittent cutting joints form parallel gap structures, and the cutting joints of the parallel gap structures form oil passing channels; and a through hole with the diameter larger than the width of the cutting seam is formed on the parallel gap structure and is used as an oil filling hole.
According to the scheme, the parallel gap structure comprises two layers of annular parallel kerfs, wherein the parallel kerfs are partially overlapped and partially staggered; two short slits are additionally arranged at the overlapping part of the two layers of parallel slits to form an S-shaped spring body, and the two short slits are oil passing channels; when vibration is generated, the S-shaped spring body generates rhythmic stretching deformation under the action of exciting force, and oil liquid is sucked and discharged in each joint along the axial direction.
According to the scheme, every two symmetrically arranged S-shaped spring bodies are in a group, and a plurality of groups of S-shaped spring bodies are uniformly distributed at intervals along the circumferential direction of the end face of the bearing bush.
According to the scheme, the parallel gap structure comprises three layers of annular parallel kerfs, the overlapped parts of the parallel kerfs form the elastic piece, the elastic piece can be bent and deformed under the action of exciting force when vibration is generated, and oil liquid is sucked and discharged in the kerfs along the axial direction.
According to the scheme, the parallel gap structure is manufactured on the bearing bush by adopting an electric spark cutting technology.
According to the scheme, the inner side of the sealing end cover is provided with the annular groove, the annular groove is internally provided with the sealing ring, and the sealing ring is made of rubber materials.
According to the scheme, a plurality of bolt holes matched with the fastening screws are formed in the sealing end cover at intervals in the circumferential direction, and the sealing end cover is fixed on the end face of the bearing bush through the fastening screws; the bolt holes and the S-shaped spring body are alternately arranged at intervals. According to the scheme, the notch is a stepped groove, and a sealed oil cavity is formed between the stepped groove and the bearing bush.
The beneficial effects of the invention are as follows:
1. the bearing lining is made of high-rigidity materials, the damping structure is additionally arranged in the bearing lining, vibration generated by various factors is transmitted to the bearing during shaft system operation, the damping structure generates rhythmic stretching deformation under the action of exciting force, oil is sucked and discharged in the gap along the axial direction to generate a piston effect, and larger damping is generated, so that energy dissipation is formed, the purpose of reducing shaft system vibration is achieved, the contradiction between high bearing capacity and low inherent frequency of the existing bearing is effectively solved, and the high bearing capacity of the water lubrication tail bearing is met while a remarkable vibration reduction effect is provided.
2. According to the invention, the damping structures are circumferentially arranged at intervals, the unprocessed materials between the damping structures can provide larger rigidity, namely, independent design of rigidity and damping is realized on the bearing bush, and enough rigidity can be maintained while large damping is provided.
3. The invention can pertinently select the distribution position and the size of the damping structure according to the actual working condition requirement, improves the working performance of the bearing, meets the requirements of each vibration reduction direction and strength, and is suitable for bearing designs in occasions with complex working environments such as ships and the like and high vibration noise requirements.
4. The invention has simple structure, strong bearing capacity and good vibration reduction effect.
Drawings
FIG. 1 is a diagram of a kinetic model of the present invention.
Fig. 2 is a schematic view of the assembly of the present invention.
Fig. 3 is a schematic view of a bearing body structure according to the first embodiment.
Fig. 4 is a schematic diagram of a damping structure according to the first embodiment.
Fig. 5 is a schematic view of a bearing structure according to a second embodiment.
Fig. 6 is a schematic diagram of a damping structure of a second embodiment.
FIG. 7 is a schematic view of the installation of a seal end cap according to the present invention.
Fig. 8 is an elevation view of a seal end cap in accordance with the present invention.
In the figure: 1. a working shaft; 2. water film lining stiffness; 3. a bearing; 4. structural rigidity of the bushing; 5. damping of the water film lining; 6. damping the bushing structure; 7. a bearing bush; 8. sealing the end cover; 9. a base; 10. a bearing liner; 11. bolt holes; 12. a damping structure; 13. an oil filling hole; 14. a support body; 15. a parallel gap structure; s-shaped spring body; 17. a fastening screw; 18. an elastic sheet; 19. a seal ring; 20. sealing the oil cavity; 21. and (5) fastening a screw.
Detailed Description
For a better understanding of the present invention, the present invention is further described below with reference to the drawings and specific examples.
The water lubrication tail bearing device with high bearing capacity and vibration reduction as shown in fig. 2 comprises a bearing lining 10, a bearing bush 7, a sealing end cover 8 and a damping structure 12, wherein the bearing lining 10 and the bearing bush 7 are of a coaxial cylindrical structure, the inner wall of the bearing lining 10 is matched with the working shaft 1, and the outer wall of the bearing lining 10 is matched with the bearing bush 7, preferably in interference fit and fixed; the outer wall of the bearing bush 7 is connected with the base 9; the sealing end cover 8 is annular and is coaxially arranged at the end part of the bearing bush 7, a notch is formed in the inner side wall of the sealing end cover 8, a sealing oil cavity 20 is formed between the notch and the end surface of the bearing bush 7, and oil is filled in the sealing oil cavity 20; the damping structure 12 and the bearing bush 7 are of an integrated structure, the damping structure 12 is of a clearance structure penetrating through two end faces of the bearing bush 7, and the clearance structure is respectively communicated with the sealed oil cavities 20 at two ends; when vibration is generated, the gap structure stretches and deforms, oil in the sealed oil cavity 20 is axially sucked and discharged in the gap structure, a piston effect is generated, energy dissipation is formed, and the purpose of reducing shafting vibration is achieved. According to the invention, oil liquids with different viscosities can be filled in the sealed oil cavity 20 according to actual needs so as to adjust the damping.
Preferably, the bearing bush 7 is made of high-rigidity materials such as carbon steel; the gap structure comprises at least two layers of intermittent kerfs which are annularly cut on the bearing bush 7, and the diameters of the intermittent kerfs of all the rings are different; the radial overlapping part of the intermittent cutting seams forms a parallel gap structure 15, and the cutting seams of the parallel gap structure 15 form an oil passing channel; a through hole with a diameter larger than the kerf width is formed in the parallel gap structure 15 as the oil filling hole 13. In this embodiment, the parallel gap structure 15 is formed by cutting slits in the bearing bush 7 using an electric spark cutting technique.
Preferably, as shown in fig. 7, an annular groove is arranged on the inner side of the sealing end cover 8, and a sealing ring 19 is arranged in the annular groove, and the sealing ring 19 is pressed to play a sealing role when being matched with the bearing bush 7. In this embodiment, two annular grooves are provided, two sealing rings 19 are correspondingly configured, the sealing rings 19 are made of rubber materials, and are arranged on the inner side and the outer side of the sealing gap 20 to play a role in strict sealing.
Preferably, as shown in fig. 8, a plurality of bolt holes 11 matched with fastening screws 17 are formed in the sealing end cover 8 at intervals in the circumferential direction, and the sealing end cover 8 is fixed on the end face of the bearing bush 7 through the fastening screws 17; the bolt holes 11 and the S-shaped spring body 16 are alternately arranged at intervals, so that the rigidity is prevented from being reduced due to the fact that the distance between the bolt holes 11 and the oil-containing gap is too short.
Preferably, the notch is a stepped groove, a sealed oil cavity 20 is formed between the stepped groove and the bearing bush 7, the sealed oil cavity 20 is filled with oil after oiling, and damping is generated during vibration to play a role in vibration reduction. Experiments show that the end seal can significantly affect the damping coefficient of the oil film damping structure 12, and the width of the seal gap 20 is inversely related to the damping coefficient, and the step groove depth is set for the working conditions of the using equipment.
Example 1
As shown in fig. 3 and 4, the parallel gap structure 15 includes two layers of annular parallel slits, and the parallel slits are partially overlapped and partially staggered; two short slits are additionally arranged at the overlapping part of the two layers of parallel slits to form an S-shaped spring body 16, and the two short slits are also oil passing channels; when vibration is generated, the S-shaped spring body 16 generates rhythmic stretching deformation under the action of exciting force, oil is sucked and discharged in each joint cutting along the axial direction, and a piston effect is generated, so that energy dissipation is formed, and the purpose of reducing shafting vibration is achieved.
Preferably, every two symmetrically arranged S-shaped spring bodies 16 are in one group, and a plurality of groups of S-shaped spring bodies 16 are uniformly distributed at intervals along the circumferential direction of the end face of the bearing bush 7. In this embodiment, the S-shaped spring bodies 16 provide greater damping but lower stiffness, while the two sets of S-shaped spring bodies 16 are not machined between them to provide greater stiffness as the support body 14.
In the present invention, the two S-shaped spring bodies 16 in the same group are symmetrically arranged so that the damping effect generated by the action of the two spring bodies is directed to the axle center. The position and the shape of the S-shaped spring body 16 are defined by three angles a, b and c, wherein the angle a is an included angle between a connecting line of the middle oil filling hole and the axle center and a central line of the S-shaped spring body 16 so as to determine the position of the S-shaped spring body 16; the angle b is an included angle between the two end points of the S-shaped spring body 16 and the connecting line of the axle center so as to determine the shape of the S-shaped spring body 16; the angle c is the included angle between the connecting line of the oil filling hole and the axis and the end point of the S-shaped spring body 16 at the same side, and can be used for adjusting the whole length of the gap so as to adjust the oil filling amount. Through the angle of adjustment three angles, the distribution position and the size of the S-shaped spring body 16 can be designed in a targeted manner, and the vibration reduction effect and the rigidity requirement in all directions are met.
Example two
As shown in fig. 5 and fig. 6, the parallel gap structure 15 includes three layers of annular parallel slits, and the overlapped portions of the parallel slits form an elastic sheet 18, so that the elastic sheet 18 can bend and deform under the action of exciting force when vibration is generated, and oil is sucked and discharged in the slits along the axial direction. The middle layer of the cutting seam is divided into a left section and a right section, and the left section and the right section form a bilaterally symmetrical double-layer elastic sheet 18 with the upper layer of the cutting seam and the lower layer of the cutting seam. The remaining features of the damping structure formed by the resilient sheet 18 are similar to those formed by the S-shaped spring body 16. The present embodiment can provide a large damping force and also has good linear characteristics under high loads.
In the present invention, the damping structure 12 is machined on the bearing bush 7 using an electric spark cutting technique; the parallel gap structures 15 are distributed along the circumferential direction of the bearing, are provided with oil filling holes 13, and can be filled with oil with different viscosities so as to adjust the damping; the material between the gaps forms an elastic variable structure, and the elastic variable structure and an oil film act together to provide damping to realize vibration reduction. The parallel gap structures 15 can provide larger damping but lower rigidity, materials among different groups of gap structures can provide larger rigidity as supporting structures, and the position and the shape can be determined by setting the position distribution angle and the shape distribution angle so as to meet the requirements of rigidity and damping in different directions.
The water lubrication tail bearing device separates the bearing function from the vibration reduction function, and a damping structure 12 is formed by cutting a joint in the bearing bush 7. The structure and the material of the bearing lining 10 serving as a bearing structure are unchanged, and high-rigidity materials such as copper or stainless steel are adopted to provide larger bearing capacity, so that the tribological properties of the bearing lining 10 are reserved, including self-lubricity, low friction and wear resistance; the damping structure 12 can provide large damping c2 as a vibration reduction structure, has higher rigidity k2 to meet the bearing requirement, realizes energy consumption vibration reduction under the condition of weakening the bearing capacity as little as possible, and can ensure the high bearing capacity of the bearing and the obvious vibration reduction effect of the bearing.
The principle of the dynamic model of the invention is shown in figure 1, and the mass of a working shaft 1 is m 1 The mass of the bearing 3 is m 2 . The working shaft 1 is not in direct contact with the bearing 3 during normal operation, and a water film is generated between the working shaft and the bearing. The working shaft 1 is contacted with a water film, and the working shaft 1 generates displacement response x when being subjected to a disturbing force F 1 Is transmitted to the bearing 3 through a water film to generate a displacement response x 2 . The water film and bearing liner will produce a water film liner stiffness 2 and a water film liner damping 5, respectively with k 1 And c 1 Indicating that this part is mainly load-bearing; the bearing bushing with damping structure can provide significant damping effect while meeting high bearing capacity, namely having enough structural rigidity 4 of the bushing and significant structural damping 6 of the bushing, respectively using k 2 And c 2 Representation, c 2 Relatively large to ensure a significant damping effect, k 2 Relatively large to ensure that the bearing capacity is sufficient.
Finally, it should be noted that the foregoing is merely a preferred embodiment of the present invention, and the present invention is not limited thereto, and although the present invention has been described in detail with reference to the embodiment, it will be apparent to those skilled in the art that modifications may be made to the technical solutions described in the foregoing embodiments, or equivalents may be substituted for some of the technical features thereof, but any modifications, equivalents, improvements or changes thereof may be made without departing from the spirit and principle of the present invention.
Claims (7)
1. The water lubrication tail bearing device is characterized by comprising a bearing lining, a bearing bush, a sealing end cover and a damping structure, wherein the bearing lining and the bearing bush are of a coaxial cylindrical structure, the inner wall of the bearing lining is matched with a working shaft, and the outer wall of the bearing lining is matched with the bearing bush; the outer wall of the bearing bush is connected with the base; the sealing end cover is annular and is coaxially arranged at the end part of the bearing bush, a notch is formed in the inner side wall of the sealing end cover, a sealing oil cavity is formed between the notch and the end face of the bearing bush, and oil is filled in the sealing oil cavity; the damping structure is a clearance structure penetrating through two end surfaces of the bearing bush, and the clearance structure is respectively communicated with the sealing oil cavities at two ends; stretching deformation is carried out through the gap structure when vibration is generated, and oil in the sealed oil cavity is axially sucked and discharged in the gap structure; the gap structure comprises at least two layers of intermittent kerfs which are annularly cut on the sealing end cover, and the diameters of the intermittent kerfs are different; the radial overlapping parts of the intermittent cutting joints form parallel gap structures, and the cutting joints of the parallel gap structures form oil passing channels; a through hole with the diameter larger than the kerf width is formed on the parallel gap structure and used as an oil filling hole; the parallel gap structure comprises two layers of annular parallel kerfs, wherein the parallel kerfs are partially overlapped and partially staggered; two short slits are additionally arranged at the overlapping part of the two layers of parallel slits to form an S-shaped spring body, and the two short slits are oil passing channels; when vibration is generated, the S-shaped spring body generates rhythmic stretching deformation under the action of exciting force, and oil liquid is sucked and discharged in each joint along the axial direction.
2. The water lubricated tail bearing device according to claim 1, wherein each two symmetrically arranged S-shaped spring bodies are in one group, and wherein a plurality of groups of S-shaped spring bodies are uniformly spaced circumferentially along the end surface of the bearing bush.
3. The water lubricated tail bearing device according to claim 1, wherein the parallel gap structure comprises three layers of annular parallel slits, the overlapped parts of the parallel slits form an elastic sheet, the elastic sheet can be bent and deformed under the action of exciting force when vibration is generated, and oil is sucked and discharged in the slits along the axial direction.
4. The water lubricated tail bearing device according to claim 1, wherein the parallel gap structure is fabricated on the bearing cartridge using an electric spark cutting technique.
5. The water lubricated tail bearing device according to claim 1, wherein the inner side of the seal end cover is provided with an annular groove, and a seal ring is arranged in the annular groove, and the seal ring is made of rubber materials.
6. The water lubricated tail bearing device according to claim 1, wherein a plurality of bolt holes matched with fastening screws are formed in the sealing end cover at intervals in the circumferential direction, and the sealing end cover is fixed on the end face of the bearing bush through the fastening screws; the bolt holes and the S-shaped spring body are alternately arranged at intervals.
7. The water lubricated tail bearing device according to claim 1, wherein the notch is a stepped groove forming a sealed oil pocket between the stepped groove and the bearing cartridge.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110581439.8A CN113404778B (en) | 2021-05-27 | 2021-05-27 | Water lubrication tail bearing device with high bearing capacity and vibration reduction |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110581439.8A CN113404778B (en) | 2021-05-27 | 2021-05-27 | Water lubrication tail bearing device with high bearing capacity and vibration reduction |
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| CN113404778A CN113404778A (en) | 2021-09-17 |
| CN113404778B true CN113404778B (en) | 2023-11-14 |
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| CN202110581439.8A Active CN113404778B (en) | 2021-05-27 | 2021-05-27 | Water lubrication tail bearing device with high bearing capacity and vibration reduction |
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| CN113833750B (en) * | 2021-09-29 | 2023-08-15 | 武汉理工大学 | Intelligent vibration reduction bearing capable of realizing water lubrication of extrusion magnetic oil film and vibration reduction method |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004278580A (en) * | 2003-03-13 | 2004-10-07 | Hiroshi Kamiyoshi | Tubular damper element |
| JP2011144924A (en) * | 2009-12-18 | 2011-07-28 | Mitsubishi Heavy Ind Ltd | Damper bearing device |
| CN103671598A (en) * | 2012-08-28 | 2014-03-26 | 艾勒根传动工程有限责任公司 | Torsional vibration damper or rotationally elastic coupling |
| CN109654124A (en) * | 2018-12-19 | 2019-04-19 | 中国科学院长春应用化学研究所 | Active spoil disposal sand water lubriucated bearing |
| JP2019100434A (en) * | 2017-11-30 | 2019-06-24 | 三菱重工業株式会社 | Bearing device and rotary machine |
| CN210637384U (en) * | 2019-10-21 | 2020-05-29 | 九江学院 | Stern shaft-stern bearing device |
| CN112513480A (en) * | 2018-09-12 | 2021-03-16 | 川崎重工业株式会社 | Damping bearing and damping |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US10697323B2 (en) * | 2016-07-21 | 2020-06-30 | Raytheon Technologies Corporation | Engine bearing damper with interrupted oil film |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004278580A (en) * | 2003-03-13 | 2004-10-07 | Hiroshi Kamiyoshi | Tubular damper element |
| JP2011144924A (en) * | 2009-12-18 | 2011-07-28 | Mitsubishi Heavy Ind Ltd | Damper bearing device |
| CN103671598A (en) * | 2012-08-28 | 2014-03-26 | 艾勒根传动工程有限责任公司 | Torsional vibration damper or rotationally elastic coupling |
| JP2019100434A (en) * | 2017-11-30 | 2019-06-24 | 三菱重工業株式会社 | Bearing device and rotary machine |
| CN112513480A (en) * | 2018-09-12 | 2021-03-16 | 川崎重工业株式会社 | Damping bearing and damping |
| CN109654124A (en) * | 2018-12-19 | 2019-04-19 | 中国科学院长春应用化学研究所 | Active spoil disposal sand water lubriucated bearing |
| CN210637384U (en) * | 2019-10-21 | 2020-05-29 | 九江学院 | Stern shaft-stern bearing device |
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| CN113404778A (en) | 2021-09-17 |
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