阅读说明：本技术 无轴轮缘推进器水润滑橡胶合金轴承及最优润滑间隙调节方法 (Water-lubricated rubber alloy bearing of shaftless rim propeller and optimal lubrication gap adjusting method ) 是由 王家序 向果 韩彦峰 肖科 贾航 王成 于 2021-05-14 设计创作，主要内容包括：本发明公开了一种无轴轮缘推进器水润滑橡胶合金轴承及最优润滑间隙调节方法,其中,无轴轮缘推进器水润滑橡胶合金轴承包括呈管状的外壳和固定套装在外壳内壁的管状的橡胶合金内衬,橡胶合金内衬内埋设有至少一个超磁致伸缩材料体,每个超磁致伸缩材料体内部和/或外部设有用于产生磁场以改变超磁致伸缩材料体磁化状态的线圈。本发明通过在橡胶合金轴承内衬埋设超磁致伸缩材料体,使得水润滑橡胶合金轴承具有一定的径向变形补偿功能,实现桨叶转子与橡胶合金内衬之间最优润滑间隙调节,从而达到提升水润滑橡胶合金轴承摩擦学性能、可靠性以及服役寿命的目的。(The invention discloses a water-lubricated rubber alloy bearing of a shaftless rim propeller and an optimal lubricating gap adjusting method, wherein the water-lubricated rubber alloy bearing of the shaftless rim propeller comprises a tubular shell and a tubular rubber alloy lining fixedly sleeved on the inner wall of the shell, at least one giant magnetostrictive material body is embedded in the rubber alloy lining, and a coil used for generating a magnetic field to change the magnetization state of the giant magnetostrictive material body is arranged inside and/or outside each giant magnetostrictive material body. According to the invention, the giant magnetostrictive material body is embedded in the inner liner of the rubber alloy bearing, so that the water-lubricated rubber alloy bearing has a certain radial deformation compensation function, and the optimal lubrication gap adjustment between the paddle rotor and the rubber alloy inner liner is realized, thereby achieving the purposes of improving the tribological performance, reliability and service life of the water-lubricated rubber alloy bearing.)

1. The utility model provides a shaftless rim propeller water lubrication rubber alloy bearing, includes pipy shell and fixed suit in the pipy rubber alloy inside lining of shell inner wall which characterized in that:

at least one giant magnetostrictive material body is embedded in the rubber alloy lining, and a coil used for generating a magnetic field to change the magnetization state of the giant magnetostrictive material body is arranged inside and/or outside each giant magnetostrictive material body.

2. A shaftless rim propeller water lubricated rubber alloy bearing according to claim 1, wherein:

the rubber alloy lining is adhered to the inner wall of the shell through mould pressing and vulcanization by a high molecular rubber alloy elastomer.

3. A shaftless rim propeller water lubricated rubber alloy bearing according to claim 2, wherein:

the number of the giant magnetostrictive material bodies is multiple, each giant magnetostrictive material body is in a long strip shape extending along the axial direction of the rubber alloy lining, and the giant magnetostrictive material bodies are uniformly arranged at intervals along the circumferential direction of the rubber alloy lining.

4. A shaftless rim propeller water lubricated rubber alloy bearing according to claim 3, wherein:

the section of the giant magnetostrictive material body is in an arc shape corresponding to the radian of the rubber alloy lining.

5. A shaftless rim propeller water lubricated rubber alloy bearing according to claim 1, wherein:

the corresponding relation between the radial thickness m of the rubber alloy lining and the inner diameter d of the rubber alloy lining is as follows, wherein the unit of the thickness m is millimeter:

metric unit, d unit is millimeter, d is more than or equal to 15 and less than 30, and m is more than or equal to 4 and less than or equal to 5; d is more than or equal to 30 and less than 55, and m is more than or equal to 6 and less than or equal to 7; d is more than or equal to 55 and less than or equal to 80, and m is more than or equal to 8 and less than or equal to 9; d is more than or equal to 80 and less than 105, m is more than or equal to 9 and less than or equal to 11; d is more than or equal to 105 and less than or equal to 135, and m is more than or equal to 1l and less than or equal to 12; d is more than or equal to 135 and less than 180, and m is more than or equal to 12 and less than or equal to 14; d is more than or equal to 180 and less than 210, and m is more than or equal to 14 and less than or equal to 15; d is more than or equal to 210 and less than 296, and m is more than or equal to 16 and less than or equal to 17; d is more than or equal to 296 and less than or equal to 340, and m is more than or equal to 16 and less than or equal to 18; d is more than or equal to 340 and less than 380, and m is more than or equal to 17 and less than or equal to 19; d is more than or equal to 380 and less than 400, m is more than or equal to 18 and less than or equal to 20; d is more than or equal to 400 and less than or equal to 500, m is more than or equal to 19 and less than or equal to 23; d is more than or equal to 500 and less than or equal to 550, and m is more than or equal to 23 and less than or equal to 25;

english unit, d unit is inch:4≤m≤5；6≤m≤7；8≤m≤9；9≤m≤11；11≤m≤13；12≤m≤14；11≤m≤13； 15≤m≤17；17≤m≤19； 19≤m≤21,20≤m≤22；21≤m≤23。

6. the shaftless rim propeller water-lubricated rubber alloy bearing of claim 5, wherein:

the axial length L of the water-lubricated rubber alloy bearing is 2-4 times of the inner diameter d of the rubber alloy lining;

the outer diameter D of the water-lubricated rubber alloy bearing is as follows:

metric unit, wherein the unit of D and m is millimeter, D +8m/3 is more than or equal to D and is less than or equal to D +8 m;

english system unit, D unit is inch, m unit is millimeter, D +2.3m/25.4 is not less than D +8 m/25.4.

7. A shaftless rim propeller water-lubricated rubber alloy bearing according to any one of claims 1 to 6, wherein:

evenly arranged along circumference on the inner wall of rubber alloy inside lining a plurality of cross sections for the water channel groove that is used for that the lubricated water passes through of convex, the water channel groove with giant magnetostrictive material body interval arrangement is located adjacent two be equipped with the cross section on the rubber alloy inside lining inner wall between the water channel groove and be convex loading end, the centre of a circle of the cross section of loading end falls on the rubber alloy inside lining axis, the water channel groove with the loading end is all followed the axial extension of rubber alloy inside lining is run through the both ends of rubber alloy inside lining, the water channel groove with be the tangent rounding off of convex connection face through the cross section between the loading end.

8. A shaftless rim propeller water lubricated rubber alloy bearing according to claim 7, wherein:

the circular arc radius of water channel groove, the circular arc radius of loading surface and the circular arc radius of connecting the face with the internal diameter d of rubber alloy inside lining between the corresponding relation as follows, wherein, d unit is millimeter or inch:

d/2 is less than or equal to d/2+ 0.5;

d/16.6 is less than or equal to (d/2+0.5)/1.4 of the arc radius of the connecting surface;

d/28 is less than or equal to (d/2+ 0.5)/2.3.

9. A water-lubricated rubber alloy bearing for a shaftless rim propeller according to claim 8, wherein a flange is fixedly provided at one end of said housing,

the corresponding relation between the diameter size of the flange plate and the inner diameter d of the rubber alloy lining is as follows:

the diameter of the flange plate is more than or equal to 1.2d and less than or equal to 3.2 d;

the corresponding relation between the axial thickness dimension of the flange plate and the radial thickness m of the rubber alloy lining is as follows:

metric unit, d and m unit are millimeter, the thickness of the flange plate is more than or equal to 1.3m and less than or equal to 2.3m,

english system unit, d unit is inch, m unit is millimeter, m/25.4 is not less than 1.9 m/25.4.

10. A method for adjusting an optimal lubrication gap of a water-lubricated rubber alloy bearing of a shaftless rim propeller, which is applied to the water-lubricated rubber alloy bearing of the shaftless rim propeller of any one of claims 1 to 9, the method comprising the steps of:

s1, taking a plurality of parameters including working conditions as input parameters of a mixed lubrication model, and obtaining the maximum unilateral elasticity-heat deformation amount of the rubber alloy lining under the current working conditions by a mixed lubrication analysis method;

s2, determining the initial compensation amount of the lubricating gap based on the maximum unilateral elastic-thermal deformation amount;

s3, converting the initial compensation amount of the lubricating gap into an external magnetic field intensity, applying the external magnetic field intensity to the giant magnetostrictive material body through the coil, and driving the rubber alloy lining to generate corresponding deformation compensation lubricating gap along the radial direction through the deformation of the giant magnetostrictive material body along the radial direction;

s4, monitoring the maximum relative jumping amount between a rotor borne by the water-lubricated rubber alloy bearing and the water-lubricated rubber alloy bearing after deformation compensation in real time, if the maximum relative jumping amount is within a preset optimal jumping threshold range, finishing adjustment, otherwise, executing the step S5;

and S5, applying a fine adjustment amount to the external magnetic field intensity, comparing the maximum relative jump amount before fine adjustment with the maximum relative jump amount after fine adjustment, further fine adjusting the external magnetic field intensity according to the comparison result until the maximum relative jump amount is within the optimal jump threshold value range, and finishing adjustment.

Technical Field

The invention relates to the technical field of water-lubricated rubber alloy bearings, in particular to a water-lubricated rubber alloy bearing of a shaftless rim propeller and an optimal lubricating clearance adjusting method.

Background

A new generation of ship power 'shaftless rim propeller' subverts the structural design of the existing electric propulsion system, and the design of the shaftless rim drive propeller is combined with a rim drive technology, so that the design becomes a subversive technology in the field of machinery and carrying engineering in China. However, variable working conditions such as nonlinear electromagnetic excitation and unsteady hydrodynamic excitation of the shaftless rim propeller put higher requirements on the comprehensive performance of a key core component, namely a water lubricated bearing. If a hard polymer water lubrication bearing is adopted in the shaftless rim propeller, the hard polymer material has weak buffering and vibration absorption capacity, and a friction pair interface has a strong rubbing effect under the strong nonlinear excitation of a blade rotor. The water-lubricated rubber alloy bearing can avoid the problems by the buffer vibration absorption effect generated by self superior self-adaptive coordinated deformation, but the interface of the liner of the water-lubricated rubber alloy bearing generates obvious transient elastic-thermal deformation due to the severe working condition of high specific pressure of the shaftless rim propeller and the variable working condition of nonlinear excitation, the effective lubrication gap between the blade rotor and the interface of the liner of the rubber alloy is expanded or reduced, the risks of blade instability, noise enhancement and friction performance deterioration are caused, and finally the propulsion efficiency and the propulsion performance of the shaftless rim propeller are reduced. Therefore, the optimal lubricating clearance adjustment of the blade rotor and the rubber alloy lining is realized by intelligently compensating the transient elasticity-thermal deformation amount through the rubber alloy bearing lining, and the method is an effective technical means for avoiding the risks. The current water lubrication rubber alloy bearing technology has the following limitations:

(1) under the conditions of high specific pressure and variable working conditions, the rubber alloy lining is easy to generate irregular transient elastic-thermal deformation with different degrees, the lubrication gap is expanded, the jumping quantity of a blade rotor is increased, the rotor instability risk is caused, and finally the propulsion performance of the shaftless rim propeller is reduced;

(2) the design of the initial lubricating gap (namely the assembly gap) of the water lubricating rubber alloy bearing depends on experience, and the initial lubricating gap can not be adjusted after the design is finished, so that the optimal lubricating gap can be achieved only under a single working condition, and the development requirements of the shaftless rim propeller under high specific pressure and variable working conditions are difficult to adapt.

Disclosure of Invention

Aiming at the defects in the prior art, the invention provides a water-lubricated rubber alloy bearing of a shaftless rim propeller and an optimal lubricating gap adjusting method.

In order to achieve the purpose, the invention adopts the following technical scheme:

according to a first aspect of the invention, the invention provides a water-lubricated rubber alloy bearing for a shaftless rim propeller, which comprises a tubular shell and a tubular rubber alloy lining fixedly sleeved on the inner wall of the shell, wherein at least one giant magnetostrictive material body is embedded in the rubber alloy lining, and a coil used for generating a magnetic field to change the magnetization state of the giant magnetostrictive material body is arranged inside and/or outside each giant magnetostrictive material body.

By adopting the structure, the giant magnetostrictive material body is embedded in the rubber alloy lining, the coil is arranged inside and/or outside the giant magnetostrictive material body, a magnetic field is generated through the coil, so that the magnetization state of the giant magnetostrictive material body is adjusted through the change of the magnetic field, the thickness of the giant magnetostrictive material body in the radial direction of the rubber alloy lining is further changed, and the corresponding part of the rubber alloy lining layer with certain resilience is forced to deform slightly along the radial direction. When the shaftless rim propeller is in service under different working conditions, the giant magnetostrictive material body embedded in the rubber alloy lining can radially expand by a certain amount, so that the lubricating gap change of the variable-working-condition service water-lubricated rubber alloy bearing caused by the irregular elasticity-thermal deformation of the rubber alloy lining is compensated, the size of the lubricating gap between the blade rotor and the bearing lining layer is adjusted, the jump instability accident of the blade rotor of the water-lubricated rubber alloy bearing in service under the variable working condition is avoided, the propelling efficiency of the shaftless rim propeller is ensured, the service safety and reliability under the variable working condition are improved, and the application range of the water-lubricated rubber alloy bearing is expanded.

Preferably, the rubber alloy lining is adhered to the inner wall of the shell through mould pressing and vulcanization by a high-molecular rubber alloy elastomer. The rubber alloy is lined with the high-molecular rubber alloy elastomer, so that the rubber alloy has excellent shock absorption, noise reduction and impact resistance, and the high-molecular rubber alloy elastomer has good resilience, and is convenient for better compensating a lubricating gap under the driving of radial deformation of a giant magnetostrictive material body; the rubber alloy lining is bonded on the inner wall of the shell through a mould pressing vulcanization process, so that the shell and the rubber alloy lining are firmly and reliably connected, and the service life of the water lubrication rubber alloy bearing is effectively prolonged.

Preferably, the number of the giant magnetostrictive material bodies is multiple, each giant magnetostrictive material body is in a long strip shape extending along the axial direction of the rubber alloy lining, and the giant magnetostrictive material bodies are uniformly arranged at intervals along the circumferential direction of the rubber alloy lining. Therefore, the plurality of giant magnetostrictive material bodies are uniformly dispersed and arranged along the circumferential direction, on one hand, giant magnetostrictive materials can be saved, on the other hand, the radial deformation of local giant magnetostrictive material bodies can be conveniently and independently controlled, and when the rubber alloy lining is locally worn, the lubricating gap between the rubber alloy lining and the rotor can be locally compensated in a targeted manner.

Preferably, the cross section of the giant magnetostrictive material body is in an arc shape corresponding to the radian of the rubber alloy lining. Therefore, after the giant magnetostrictive material body radially deforms, the inner wall of the rubber alloy lining at the corresponding part can also keep in a circular arc shape, and the rubber alloy lining and the rotor are better matched to an optimal lubricating gap.

Preferably, the correspondence between the radial thickness m of the rubber alloy lining and the inner diameter d of the rubber alloy lining is as follows, wherein the thickness m is in millimeters:

metric unit, d unit is millimeter, d is more than or equal to 15 and less than 30, and m is more than or equal to 4 and less than or equal to 5; d is more than or equal to 30 and less than 55, and m is more than or equal to 6 and less than or equal to 7; d is more than or equal to 55 and less than or equal to 80, and m is more than or equal to 8 and less than or equal to 9; d is more than or equal to 80 and less than 105, m is more than or equal to 9 and less than or equal to 11; d is more than or equal to 105 and less than or equal to 135, and m is more than or equal to 1l and less than or equal to 12; d is more than or equal to 135 and less than 180, and m is more than or equal to 12 and less than or equal to 14; d is more than or equal to 180 and less than 210, and m is more than or equal to 14 and less than or equal to 15; d is more than or equal to 210 and less than 296, and m is more than or equal to 16 and less than or equal to 17; d is more than or equal to 296 and less than or equal to 340, and m is more than or equal to 16 and less than or equal to 18; d is more than or equal to 340 and less than 380, and m is more than or equal to 17 and less than or equal to 19; d is more than or equal to 380 and less than 400, m is more than or equal to 18 and less than or equal to 20; d is more than or equal to 400 and less than or equal to 500, m is more than or equal to 19 and less than or equal to 23; d is more than or equal to 500 and less than or equal to 550, and m is more than or equal to 23 and less than or equal to 25;

english unit, d unit is inch:4≤m≤5；6≤m≤7；8≤m≤9；9≤m≤11；11≤m≤13；12≤m≤14；11≤m≤13； 15≤m≤17；17≤m≤19； 20≤m≤22；21≤m≤23。

because the relation between the thickness and the radius of the inner liner of the existing water-lubricated rubber alloy bearing is difficult to consider, the relation between the buffer vibration absorption, the bearing capacity and the self-adaptive coordinated deformation, the radial thickness m of the rubber alloy inner liner and the inner diameter d of the rubber alloy inner liner adopt the corresponding relation, the influence of the radial thickness of the metal alloy inner liner on the bearing capacity and the shock resistance of the bearing is comprehensively considered, and the comprehensive performance of the water-lubricated rubber alloy bearing is improved and the service life of the water-lubricated rubber alloy bearing is prolonged by adopting the corresponding thickness of the rubber alloy inner liner according to the water-lubricated rubber alloy bearings with different specifications.

Preferably, the axial length L of the water-lubricated rubber alloy bearing is 2-4 times the inner diameter d of the rubber alloy lining;

the outer diameter D of the water-lubricated rubber alloy bearing is as follows:

metric unit, wherein the unit of D and m is millimeter, D +8m/3 is more than or equal to D and is less than or equal to D +8 m;

english system unit, D unit is inch, m unit is millimeter, D +2.3m/25.4 is not less than D +8 m/25.4.

Preferably, evenly arranged along circumference on the inner wall of rubber alloy inside lining is a plurality of cross sections for the water channel groove that the lubricated water of being used for of convex passes through, the water channel groove with giant magnetostrictive material body interval arrangement is located adjacent two be equipped with the cross section for convex loading end on the rubber alloy inside lining inner wall between the water channel groove, the centre of a circle of the cross section of loading end falls on the rubber alloy inside lining axis, the water channel groove with the loading end is all followed the axial extension of rubber alloy inside lining and is run through the both ends of rubber alloy inside lining, the water channel groove with be the tangent rounding off of the face of connecting that is convex through the cross section between the loading end. Compared with the prior art that the water channel grooves adopt straight grooves, the water-lubricated rubber alloy bearing has the advantages that the capability of draining silt and impurities of the water-lubricated rubber alloy bearing can be effectively enhanced, the heat dissipation performance of the rubber alloy lining is improved, the friction and wear speed of the rubber alloy lining is reduced, the elastic fluid dynamic pressure lubrication is more easily generated, a water film bearing is formed between the rubber bearing lining and a rotor, the friction and wear are reduced, the service life of the water-lubricated rubber alloy bearing is prolonged, and the running reliability and the propelling efficiency of the shaftless rim propeller are improved.

Preferably, the corresponding relationship among the circular arc radius of the water channel groove, the circular arc radius of the bearing surface, the circular arc radius of the connecting surface and the inner diameter d of the rubber alloy lining is as follows, wherein d is a unit of millimeter or inch:

d/2 is less than or equal to d/2+ 0.5;

d/16.6 is less than or equal to (d/2+0.5)/1.4 of the arc radius of the connecting surface;

d/28 is less than or equal to (d/2+ 0.5)/2.3.

Preferably, a flange is fixedly arranged at one end of the outer shell, and the corresponding relation between the diameter size of the flange and the inner diameter d of the rubber alloy lining is as follows:

the diameter of the flange plate is more than or equal to 1.2d and less than or equal to 3.2 d;

the corresponding relation between the axial thickness dimension of the flange plate and the radial thickness m of the rubber alloy lining is as follows:

metric unit, d and m unit are millimeter, the thickness of the flange plate is more than or equal to 1.3m and less than or equal to 2.3m,

english system unit, d unit is inch, m unit is millimeter, m/25.4 is not less than 1.9 m/25.4.

According to a second aspect of the present invention, the present invention provides an optimal lubrication gap adjustment method for a water-lubricated rubber alloy bearing of a shaftless rim propeller, which is applied to the water-lubricated rubber alloy bearing of the shaftless rim propeller according to any one of the above first aspects, and the method comprises the following steps:

s1, taking a plurality of parameters including working conditions as input parameters of a mixed lubrication model, and obtaining the maximum unilateral elasticity-heat deformation amount of the rubber alloy lining under the current working conditions by a mixed lubrication analysis method;

s2, determining the initial compensation amount of the lubricating gap based on the maximum unilateral elastic-thermal deformation amount;

s3, converting the initial compensation amount of the lubricating gap into an external magnetic field intensity, applying the external magnetic field intensity to the giant magnetostrictive material body through the coil, and driving the rubber alloy lining to generate corresponding deformation compensation lubricating gap along the radial direction through the deformation of the giant magnetostrictive material body along the radial direction;

s4, monitoring the maximum relative jumping amount between a rotor borne by the water-lubricated rubber alloy bearing and the water-lubricated rubber alloy bearing after deformation compensation in real time, if the maximum relative jumping amount is within a preset optimal jumping threshold range, finishing adjustment, otherwise, executing the step S5;

and S5, applying a fine adjustment amount to the external magnetic field intensity, comparing the maximum relative jump amount before fine adjustment with the maximum relative jump amount after fine adjustment, further fine adjusting the external magnetic field intensity according to the comparison result until the maximum relative jump amount is within the optimal jump threshold value range, and finishing adjustment.

The optimal lubricating clearance adjusting method designs a corresponding control algorithm to coordinate the relationship between the maximum unilateral elasticity-thermal deformation amount, the service working condition of the bearing and the radial compensation amount, and provides a theoretical basis for the dynamic optimal lubricating clearance adjustment of the water-lubricated rubber alloy bearing of the shaftless rim propeller under the conditions of high specific pressure and variable working conditions.

The invention has the beneficial effects that:

the invention provides a water-lubricated rubber alloy bearing of a shaftless rim propeller with a radial deformation compensation function by embedding a giant magnetostrictive material body in a rubber alloy bearing lining, which can enable a lubrication gap between the rubber alloy bearing lining and a rotor borne by the rubber alloy bearing lining to be always in an optimal state, thereby achieving the purposes of improving the tribological performance, the reliability and the service life of the water-lubricated rubber alloy bearing, effectively overcoming the problems of increased jumping quantity of a blade rotor, the risk of rotor instability and the reduction of the propulsion performance of the shaftless rim propeller caused by the irregular transient elastic-thermal deformation with different degrees of easiness of the rubber alloy lining under the conditions of high specific pressure and variable working conditions, adapting to the development requirements of the conditions of high specific pressure and variable working conditions of the shaftless rim propeller, and providing an adaptive optimal lubrication gap adjustment method based on the water-lubricated rubber alloy bearing of the shaftless rim propeller with adjustable lubrication gap The method is carried out.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

In order to more clearly illustrate the detailed description of the invention or the technical solutions in the prior art, the drawings that are needed in the detailed description of the invention or the prior art will be briefly described below. Throughout the drawings, like elements or portions are generally identified by like reference numerals. In the drawings, elements or portions are not necessarily drawn to scale.

FIG. 1(a) is a dynamic contact load law simulation diagram of a water-lubricated rubber alloy bearing with different radius gaps when the unbalance amount of a rotor is 20 μm in the invention;

FIG. 1(b) is a dynamic contact load law simulation diagram of a water-lubricated rubber alloy bearing with different radius gaps when the unbalance amount of a rotor is 30 μm in the invention;

FIG. 2 is a schematic illustration of the fit between the water lubricated rubber alloy bearing and the rotor of the shaftless rim propeller in one embodiment of the present invention;

FIG. 3 is a cross-sectional view A-A of FIG. 2 (rotor not shown);

fig. 4 is a flow chart of an optimal lubrication gap adjustment method for a water-lubricated rubber alloy bearing of a shaftless rim thruster according to an embodiment of the present invention.

Detailed Description

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The following examples are only for illustrating the technical solutions of the present invention more clearly, and therefore are only examples, and the protection scope of the present invention is not limited thereby.

It is to be noted that, unless otherwise specified, technical or scientific terms used herein shall have the ordinary meaning as understood by those skilled in the art to which the invention pertains.

In the description of the present application, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.

Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through intervening media. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

Analyzing the influence of the radius clearance on the dynamic tribology performance of the water-lubricated rubber alloy bearing:

periodic disturbance caused by unbalanced rotor dynamic load is considered, the influence of a lubricating gap on tribology performance is represented by comparing transient contact loads of water-lubricated rubber alloy bearings in gaps with different radiuses, and a table 1 is a scaling model calculation parameter. As can be seen from fig. 1(a) and 1(b), the optimum radial clearances of the water-lubricated rubber alloy bearings are both about 0.06mm when the rotor unbalance amounts to 20 μm and 30 μm, respectively. The figure demonstrates that: the purpose of optimizing the dynamic tribology performance of the water-lubricated rubber alloy bearing can be achieved by adjusting the lubrication gap of the water-lubricated rubber alloy bearing. Therefore, the dynamic tribology performance under the variable working condition is optimized by intelligently compensating the deformation of the water-lubricated rubber alloy bearing of the shaftless rim propeller, and the method has feasibility in thinking and methods.

TABLE 1 scaling model calculation parameters

Parameter(s)	Value of	Parameter(s)	Value of
				Inner diameter of bearing	22.5mm	Rotational speed	1000rpm
Bearing outside diameter	25mm	Load(s)	2000N
				Bearing length	80mm	Surface roughness	1.0μm
Modulus of elasticity of bearing	30MPa	Orientation of surface texture	Each direction of the lightSame property
				Viscosity of water	0.001Pa.s

As shown in fig. 2-3, the embodiment of the present invention provides a water-lubricated rubber alloy bearing for a shaftless rim propeller, which includes a tubular housing 1 and a tubular rubber alloy liner 2 fixedly sleeved on an inner wall of the housing 1, where the housing 1 may specifically be a copper pipe, and at least one giant magnetostrictive material body 3 is embedded in the rubber alloy liner 2. Preferably, in the present embodiment, as shown in fig. 3, a plurality of giant magnetostrictive material bodies 3 are provided, each giant magnetostrictive material body 3 is in a long strip shape extending along the axial direction of the rubber alloy liner 2, and the plurality of giant magnetostrictive material bodies 3 are uniformly spaced along the circumferential direction of the rubber alloy liner 2. Each of the bodies 3 is internally provided with a coil 4 for generating a magnetic field to change the magnetization state of the body 3.

In other embodiments, the coil 4 may be wound outside the body 3 of giant magnetostrictive material, or the coil 4 may be provided inside and outside the body 3 of giant magnetostrictive material.

In one embodiment, the rubber alloy lining 2 is adhered to the inner wall of the outer shell 1 by a high-molecular rubber alloy elastomer through mould pressing and vulcanization. The preparation process and the mold pressing and vulcanizing process of the polymer rubber alloy elastomer are prior art, and are not described herein again. The preparation process of the polymer rubber alloy elastomer can refer to the preparation process of the water-lubricated rubber alloy bushing in patent document CN101334069B, and is not described herein again.

In one embodiment, as shown in figure 3, the cross-section of the body of giant magnetostrictive material 3 is curved to conform to the curvature of the rubber alloy lining 2. After the giant magnetostrictive material body 3 is radially deformed, the inner wall of the rubber alloy lining 2 at the corresponding part can also keep in a circular arc shape, so that the rubber alloy lining 2 and the rotor 100 are better adapted to an optimal lubricating gap.

In one embodiment, the correspondence between the radial thickness m of the rubber alloy liner 2 and the inner diameter d of the rubber alloy liner 2 is as follows, where the thickness m is in millimeters:

metric unit, d unit is millimeter, d is more than or equal to 15 and less than 30, and m is more than or equal to 4 and less than or equal to 5; d is more than or equal to 30 and less than 55, and m is more than or equal to 6 and less than or equal to 7; d is more than or equal to 55 and less than or equal to 80, and m is more than or equal to 8 and less than or equal to 9; d is more than or equal to 80 and less than 105, m is more than or equal to 9 and less than or equal to 11; d is more than or equal to 105 and less than or equal to 135, and m is more than or equal to 1l and less than or equal to 12; d is more than or equal to 135 and less than 180, and m is more than or equal to 12 and less than or equal to 14; d is more than or equal to 180 and less than 210, and m is more than or equal to 14 and less than or equal to 15; d is more than or equal to 210 and less than 296, and m is more than or equal to 16 and less than or equal to 17; d is more than or equal to 296 and less than or equal to 340, and m is more than or equal to 16 and less than or equal to 18; d is more than or equal to 340 and less than 380, and m is more than or equal to 17 and less than or equal to 19; d is more than or equal to 380 and less than 400, m is more than or equal to 18 and less than or equal to 20; d is more than or equal to 400 and less than or equal to 500, m is more than or equal to 19 and less than or equal to 23; d is more than or equal to 500 and less than or equal to 550, and m is more than or equal to 23 and less than or equal to 25;

english unit, d unit is inch:4≤m≤5；6≤m≤7；8≤m≤9；9≤m≤11；11≤m≤13；12≤m≤14；11≤m≤13； 15≤m≤17；17≤m≤19； 19≤m≤21,20≤m≤22；21≤m≤23。

because the relation between the liner thickness and the radius size of the existing water-lubricated rubber alloy bearing is difficult to consider, the relation between the buffer vibration absorption, the bearing capacity and the self-adaptive coordinated deformation, the radial thickness m of the rubber alloy liner 2 and the inner diameter d of the rubber alloy liner 2 adopt the corresponding relation, the influence of the radial thickness of the metal alloy liner on the bearing capacity and the shock resistance of the bearing is comprehensively considered, and the comprehensive performance of the water-lubricated rubber alloy bearing is improved and the service life of the water-lubricated rubber alloy bearing is prolonged by adopting the corresponding thickness of the rubber alloy liner 2 according to the water-lubricated rubber alloy bearings with different specifications.

In one embodiment, the axial length L of the water-lubricated rubber alloy bearing is 2 to 4 times the inner diameter d of the rubber alloy liner 2;

the outer diameter D of the water-lubricated rubber alloy bearing is as follows:

metric unit, wherein the unit of D and m is millimeter, D +8m/3 is more than or equal to D and is less than or equal to D +8 m;

english system unit, D unit is inch, m unit is millimeter, D +2.3m/25.4 is not less than D +8 m/25.4.

In one embodiment, as shown in fig. 3, a plurality of water channel grooves 5 with circular arc cross sections for lubricating water to pass through are uniformly arranged on the inner wall of the rubber alloy liner 2 along the circumferential direction, the water channel grooves 5 and the giant magnetostrictive material bodies 3 are arranged at intervals, a bearing surface 6 with circular arc cross sections is arranged on the inner wall of the rubber alloy liner 2 between two adjacent water channel grooves 5, the circle center of the cross section of the bearing surface 6 is located on the axis of the rubber alloy liner 2, the water channel grooves 5 and the bearing surface 6 both extend along the axial direction of the rubber alloy liner 2 and penetrate through two ends of the rubber alloy liner 2, and the water channel grooves 5 and the bearing surface 6 are in tangential smooth transition through a connecting surface 7 with circular arc cross sections. The circular arc-shaped water channel grooves 5 are adopted, the circular arc-shaped bearing surfaces 6 are arranged on the inner walls of the rubber alloy linings 2 between the adjacent water channel grooves 5 in an axially extending mode, and smooth transition is achieved between the water channel grooves 5 and the circular arc-shaped bearing surfaces 6 through the circular arc-shaped connecting surfaces 7.

In one embodiment, the correspondence between the arc radius of the channel groove 5, the arc radius of the bearing surface 6, and the arc radius of the joint surface 7 and the inner diameter d of the rubber alloy liner 2 is as follows, wherein d is in millimeters or inches:

d/2 is less than or equal to d/2+ 0.5;

d/16.6 is less than or equal to (d/2+0.5)/1.4 of the arc radius of the connecting surface;

d/28 is less than or equal to (d/2+ 0.5)/2.3.

In one embodiment, as shown in fig. 3, a flange 8 is fixedly disposed at one end of the housing 1, the flange 8 may be integrally formed with the housing 1, a plurality of mounting holes 9 are formed in the flange 8 and evenly spaced along the circumferential direction, and the diameter of the flange 8 corresponds to the inner diameter d of the rubber alloy lining 2 as follows:

the diameter of the flange plate is more than or equal to 1.2d and less than or equal to 3.2 d;

the correspondence between the axial thickness dimension of the flange 8 and the radial thickness m of the rubber alloy lining 2 is as follows:

metric unit, d and m unit are millimeter, the thickness of the flange plate is more than or equal to 1.3m and less than or equal to 2.3m,

english system unit, d unit is inch, m unit is millimeter, m/25.4 is not less than 1.9 m/25.4.

As shown in fig. 2 to 4, an embodiment of the present invention further provides an optimal lubrication gap adjustment method for a water-lubricated rubber alloy bearing of a shaftless rim thruster, which is applied to the water-lubricated rubber alloy bearing of the shaftless rim thruster in any of the above embodiments, and the method includes the following steps:

s1, taking a plurality of parameters including working conditions as input parameters of a mixed lubrication model, and obtaining the maximum unilateral elasticity-heat deformation amount of the rubber alloy lining 2 under the current working conditions by a mixed lubrication analysis method;

when the lubricating clearance of the water-lubricated rubber alloy bearing of the shaftless rim propeller needs to be adjusted, the maximum unilateral elasticity-thermal deformation amount of the rubber alloy lining 2 under the current working condition is calculated by a lubrication analysis method. Specifically, the plurality of input parameters in this step may include material properties of the rubber alloy lining 2, thickness of the rubber alloy lining 2, constraint conditions, deep water pressure, and the like, in addition to the working conditions. The mixed lubrication analysis method is a common analysis method in the field, wherein the used mixed lubrication model belongs to the prior art and is not described herein again.

S2, determining the initial compensation amount of the lubricating gap based on the maximum unilateral elastic-thermal deformation amount;

because the irregular elastic-thermal deformation of the rubber alloy lining 2 under the variable working condition service needs to be compensated through the micro deformation of the giant magnetostrictive material body 3, the initial compensation amount of the lubricating gap is the maximum unilateral elastic-thermal deformation amount obtained through calculation.

S3, converting the initial compensation amount of the lubricating gap into an external magnetic field intensity, applying the external magnetic field intensity to the giant magnetostrictive material body 3 through the coil 4, and driving the rubber alloy lining 2 to generate corresponding deformation compensation lubricating gap along the radial direction through the deformation of the giant magnetostrictive material body 3 along the radial direction;

after the initial compensation amount of the lubricating gap needing to be compensated is determined, a control system is required to control a magnetic field generated by a coil 4 of the giant magnetostrictive material body 3, and the stretching amount of the giant magnetostrictive material body 3 is controlled by changing the magnetic field, so that the rubber alloy lining 2 is driven by stretching of the giant magnetostrictive material body 3 to generate a deformation compensation lubricating gap along the radial direction. Therefore, the determined initial compensation amount of the lubricating gap needs to be converted into the intensity of the external magnetic field applied to the giant magnetostrictive material body 3 and applied to the giant magnetostrictive material body 3, so that the giant magnetostrictive material body 3 deforms along the radial direction to drive the rubber alloy lining 2 to deform correspondingly along the radial direction to compensate the lubricating gap.

S4, monitoring the maximum relative runout amount between the rotor 100 carried by the water-lubricated rubber alloy bearing and the water-lubricated rubber alloy bearing after deformation compensation in real time, if the maximum relative runout amount is within a preset optimal runout threshold range, finishing adjustment, otherwise, executing the step S5;

after the deformation compensation is performed according to the initial deformation compensation amount, the lubrication gap between the rubber alloy liner 2 and the rotor 100 may reach the initial lubrication gap, but the initial lubrication gap is not necessarily the optimal gap, so it is necessary to continuously monitor in real time whether the maximum relative runout amount between the rotor 100 and the water-lubricated rubber alloy bearing, which are carried by the water-lubricated rubber alloy bearing after the deformation compensation, is within the preset optimal runout threshold range, if so, the adjustment is ended, and if not, the lubrication gap compensation amount needs to be further adjusted so that the lubrication gap reaches the optimal state. Specifically, the real-time monitoring of the maximum relative run-out between the rotor 100 carried by the water-lubricated rubber alloy bearing and the water-lubricated rubber alloy bearing can be monitored by using the displacement sensor 10, as shown in fig. 2, and the displacement sensor 10 can be fixedly installed at one end of the water-lubricated rubber alloy bearing or installed inside the water-lubricated rubber alloy bearing. The determination of the optimal run-out threshold range depends on the air gap between the rotor 100 and the stator of the integrated electric machine used to drive the rotor 100, in relation to the performance of the integrated electric machine itself.

And S5, applying a fine adjustment amount to the intensity of the applied magnetic field, comparing the maximum relative jump amount before fine adjustment with the maximum relative jump amount after fine adjustment, further fine adjusting the intensity of the applied magnetic field according to the comparison result until the maximum relative jump amount is within the range of the optimal jump threshold value, and finishing adjustment.

In the process of continuously adjusting the lubricating gap, applying a fine adjustment amount to the intensity of the applied magnetic field each time, wherein the fine adjustment amount can be specifically set according to specific conditions, after the fine adjustment amount is applied, continuously driving the rubber alloy lining 2 to deform and compensate the lubricating gap along the radial direction through the telescopic deformation of the giant magnetostrictive material body 3, comparing the maximum relative jumping amount before the fine adjustment with the maximum relative jumping amount after the fine adjustment, further finely adjusting the intensity of the applied magnetic field according to the comparison result until the maximum relative jumping amount is within the optimal jumping threshold range, and then finishing the adjustment.

The optimal lubricating clearance adjusting method designs a corresponding control algorithm to coordinate the relationship between the maximum unilateral elasticity-thermal deformation amount, the service working condition of the bearing and the radial compensation amount, and provides a theoretical basis for the dynamic optimal lubricating clearance adjustment of the water-lubricated rubber alloy bearing of the shaftless rim propeller under the conditions of high specific pressure and variable working conditions.

In the description of the present invention, numerous specific details are set forth. It is understood, however, that embodiments of the invention may be practiced without these specific details. In some instances, well-known methods, structures and techniques have not been shown in detail in order not to obscure an understanding of this description.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention, and they should be construed as being included in the following claims and description.