CN113790206A

CN113790206A - Composite material transmission shaft and sliding bearing thereof

Info

Publication number: CN113790206A
Application number: CN202111078951.7A
Authority: CN
Inventors: 尹忠慰
Original assignee: Shanghai Lianyi Bearing Technology Co ltd
Current assignee: Shanghai Lianyi Bearing Technology Co ltd
Priority date: 2021-09-15
Filing date: 2021-09-15
Publication date: 2021-12-14

Abstract

A composite material transmission shaft and a sliding bearing thereof relate to the technical field of wind power generation, in particular to application of carbon fiber and glass fiber on a wind power main shaft and application of a sliding bearing matched with the carbon fiber and the glass fiber. The shaft body is formed by winding a plurality of layers of composite material layers; the axial direction of the shaft body is 0 degree, the winding angles of the composite material layers include 0 degree, 15 degrees, 45 degrees and 90 degrees, and the difference value of the absolute values of the winding angles of the adjacent composite material layers is smaller than 90 degrees. The shaft body can bear multidirectional stress in actual work, interlayer stress is reduced, and layering damage and deformation of the shaft body are avoided. In addition, the rolling bearing matched with the rolling bearing has the defects of limited service life, large volume, large vibration and noise and sensitivity to foreign matters such as metal chips and the like. In order to improve the power torque density of the wind turbine generator, reduce the unit kilowatt weight, improve the conversion efficiency and reduce the operation and maintenance cost, the sliding bearing is a better choice to replace the rolling bearing.

Description

Composite material transmission shaft and sliding bearing thereof

Technical Field

The invention relates to the technical field of wind power generation, in particular to a composite material transmission shaft and a sliding bearing thereof. In particular to the application of carbon fiber and glass fiber on a wind power main shaft and the application of a sliding bearing matched with the same.

Background

When the wind power main shaft is in operation, the wind power main shaft is used as a core component in a wind generating set, mainly the rotating moment on a generator blade is transmitted to a gear box, and the requirements on the torque transmission capacity, the bending resistance capacity, the impact resistance capacity and the like of the main shaft are high. The main shaft is generally made of steel materials, the diameter of the transmission shaft is large, the weight of the transmission shaft is large, due to the fact that the specific modulus and specific rigidity of metal materials are low, machining, arrangement, installation and debugging of the transmission shaft are very difficult, and the main shaft is always developed by finding materials with higher strength, lighter weight and the same structure to replace steel materials.

Meanwhile, the rolling bearing has the defects of limited service life, large volume, large vibration and noise and sensitivity to foreign matters such as metal chips and the like. In order to improve the power torque density of the wind turbine generator, reduce the unit kilowatt weight, improve the conversion efficiency and reduce the operation and maintenance cost, the adoption of the sliding bearing to replace the rolling bearing is a consistent pursuit of the fan manufacturers at home and abroad.

Disclosure of Invention

Aiming at the defects in the prior art, the invention provides a composite material transmission shaft and a sliding bearing thereof, and the specific scheme is as follows:

a composite material transmission shaft comprises a shaft body, wherein the shaft body is formed by winding a plurality of composite material layers;

the axial direction of the shaft body is 0 degree, the winding angles of the composite material layers include 0 degree, 15 degrees, 45 degrees and 90 degrees, and the difference value of the absolute values of the winding angles of the adjacent composite material layers is smaller than 90 degrees.

Further preferably, when the winding angle of the composite material layer is ± 45 °, the winding angle of the adjacent composite material layer is 0 ° or ± 15 ° or 90 °;

when the winding angle of the composite material layer is 0 degree, the winding angle of the adjacent composite material layers is +/-45 degrees or +/-15 degrees;

when the winding angle of the composite material layers is 90 degrees, the winding angle of the adjacent composite material layers is +/-45 degrees or +/-15 degrees.

Further preferably, the preparation material of the composite material layer comprises a matrix phase and a reinforcing phase, the matrix phase comprises epoxy resin and unsaturated polyester, and the reinforcing phase comprises carbon fiber, glass fiber, aramid fiber, basalt fiber and kenaf fiber.

Preferably, a metal piece is arranged on the side wall of the shaft body close to the end part of the shaft body and along the circumferential direction of the shaft body, and the metal piece is wrapped among the multiple layers of composite material layers;

the connecting hole is formed in the end face of the shaft body in the axial direction of the shaft body, and one side, close to the shaft body, of the connecting hole extends along the direction close to the shaft body so that part of the connecting hole penetrates through the metal piece.

Further preferably, a positioning structure for preventing the metal piece and the shaft body from moving relatively is arranged on a contact side surface of the shaft body and the metal piece.

Further preferably, one end of the shaft body is connected with a driving device to serve as a first end, and the other end of the shaft body is connected with a transmission device to serve as a second end;

the outer diameter of the shaft body close to the first end portion is larger than the outer diameter of the shaft body close to the second end portion.

Further preferably, an inner diameter of the shaft body near the first end portion is larger than an inner diameter of the shaft body near the second end portion.

Further preferably, a shoulder protruding away from the shaft body is arranged on the outer side wall of the shaft body along the circumferential direction of the shaft body.

The invention also provides a sliding bearing which is connected with the composite material in a transmission fit mode, wherein the sliding bearing comprises a thrust bearing and/or a radial bearing.

Further preferably, when the sliding bearing is the thrust bearing, a bearing bush of the thrust bearing is in abutting fit with the shaft shoulder;

when the sliding bearing is the radial bearing, the bearing bushes of the radial bearing are uniformly or non-uniformly distributed along the circumferential direction of the shaft body.

Compared with the prior art, the invention has the following beneficial effects:

(1) because the paired winding angles of +/-45 degrees and the paired winding angles of 0 degree and 90 degrees are in a cross shape, the axial stress and the radial stress of the shaft body are the same. In actual operation, if the shaft body is made by winding at the above-mentioned paired winding angles, the composite material layer of the shaft body is easily damaged by delamination under the action of interlaminar stress. In order to ensure that the shaft body bears multidirectional stress, the paired winding angles of +45 degrees and-45 degrees are separated by 0 degrees or +/-15 degrees or 90 degrees, and the paired winding angles of 0 degrees and 90 degrees are separated by +45 degrees or-45 degrees or +/-15 degrees, so that the shaft body can bear the multidirectional stress in actual work, the interlayer stress is reduced, and the layered damage is avoided.

(2) The sliding bearing adopts a block structure, is convenient to disassemble and replace, and both the radial pad and the thrust pad can adopt tilting pad structures. The tilting pad can freely swing along with the difference of rotating speed, load and bearing temperature when in work, and a plurality of oil wedges are formed around the shaft diameter. The tilting pad supporting bearing is generally composed of 3-5 or more pad blocks capable of freely tilting on a pivot point, and has high stability. In addition, the tilting pad supporting bearing also has the advantages of large supporting flexibility, good vibration energy absorption, large bearing capacity, low power consumption and the like.

(3) When the shaft body shakes or deviates from the original installation axis, the elastic body is arranged below the thrust pad, and the elastic body generates certain deformation when being pressed, so that the thrust pad is inclined according to the deformation amount, and an oil film is formed; and the pad swings freely along with the change of the rotating speed, the load and the bearing temperature, and has better self-adaptive capacity, thereby having higher stability. Meanwhile, due to the buffering capacity of the elastic part, the bearing can bear certain impact load; therefore, excessive abrasion caused by eccentric wear or impact due to uneven stress of the thrust bearing is well avoided, and the service life of the thrust bearing is effectively prolonged. Even in the service period of the thrust bearing, when the thrust pad is damaged, the thrust bearing does not need to be integrally disassembled and replaced, and only the damaged fixed plate or thrust pad needs to be disassembled, replaced or maintained, so that the maintenance cost of the thrust bearing is reduced, and the maintenance efficiency is improved.

Drawings

FIG. 1 is a general schematic view of a shaft body according to the present invention;

FIG. 2 is a general schematic view of the shaft body and the sliding bearing in a fit connection according to the present invention;

FIG. 3 is a schematic view showing the radial tiles being unevenly distributed along the circumference of the shaft body;

FIG. 4 is a schematic view showing radial tiles uniformly distributed along the circumference of the shaft body;

FIG. 5 is a schematic view showing the thrust shoe mounted to the bearing housing;

FIG. 6 is a schematic cross-sectional view showing a tiltable structure;

fig. 7 is another schematic cross-sectional view showing a tiltable structure.

Reference numerals: 1. a fixing plate; 11. a first groove; 12. a first oil hole; 13. a second oil groove; 2. a thrust pad; 21. a second groove; 22. a second oil hole; 23. a second oil reservoir chamber; 24. a first oil groove; 3. a limiting groove; 4. a limiting member; 41. a limiting part; 5. an elastic member; 51. a first oil reservoir chamber; 6. positioning blocks; 7. a wear layer; 8. a bearing seat; 100. a radial bearing; 200. a thrust bearing; 300. a shaft body; 301. a first end portion; 302. a second end portion; 303. connecting holes; 304. and a shaft shoulder.

Detailed Description

The present invention will be described in further detail with reference to examples and drawings, but the present invention is not limited to these examples.

As shown in fig. 1, a composite material propeller shaft includes a shaft body 300, and the shaft body 300 is formed by winding a plurality of composite material layers. The preparation material of the composite material layer comprises a matrix phase and a reinforcing phase, wherein the matrix phase comprises epoxy resin and unsaturated polyester, and the reinforcing phase comprises carbon fiber, glass fiber, aramid fiber, basalt fiber and kenaf fiber.

The axial direction of the shaft body 300 is 0 degree, and the winding angles of the composite material layers include 0 degree, 15 degrees, 45 degrees and 90 degrees. Wherein, the winding angle of 0 degree is beneficial to reducing the relative movement between the cross sections; the winding angle of ± 45 ° can improve the torsion resistance of the shaft body 300. In an initial torsion state, the 90-degree winding angle has the function of resisting stress, but the torsion resistance is reduced along with the increase of the torsion moment; when the winding angle is in the range of 15 ° to 50 °, the torsion angle per unit length of the shaft body 300 is small, so that the rigidity of the propeller shaft can be enhanced. The stress is used to represent an internal force generated by interaction between layers in the shaft body 300 when the shaft body 300 is deformed due to external factors (stress, humidity, temperature field change, etc.). The internal force acts against the external factors, and attempts to restore the shaft body 300 from the post-deformation position to the pre-deformation position. It is understood that the larger the deformation degree of the shaft body 300, the larger the interlayer stress; the smaller the deformation degree of the shaft body 300, the smaller the interlayer stress.

In an exemplary embodiment, the difference in absolute values of the wrap angles of adjacent composite layers is less than 90 °. For example: when the winding angle of the composite material layer is +/-45 degrees, the winding angle of the adjacent composite material layer is 0 degree or +/-15 degrees or 90 degrees; when the winding angle of the composite material layer is 0 degree, the winding angle of the adjacent composite material layers is +/-45 degrees or +/-15 degrees; when the winding angle of the composite material layer is 90 degrees, the winding angle of the adjacent composite material layers is +/-45 degrees or +/-15 degrees.

Since the ± 45 ° paired winding angles and the 0 ° and 90 ° paired winding angles are cross-shaped, the axial and radial stresses applied to the shaft body 300 are the same. In actual operation, if the shaft body 300 is formed by winding at the above-mentioned paired winding angles, the composite material layer of the shaft body 300 is easily damaged by delamination under the action of interlayer stress. In order to ensure that the shaft body 300 bears multidirectional stress, the paired winding angles of +45 degrees and-45 degrees are separated by 0 degrees or +/-15 degrees or 90 degrees, and the paired winding angles of 0 degrees and 90 degrees are separated by +45 degrees or-45 degrees or +/-15 degrees, so that the shaft body 300 can bear the multidirectional stress in actual work, the interlayer stress is reduced, and the layered damage is avoided

It should be particularly noted that the winding process commonly used in the prior art is difficult to realize a winding angle of 0 °, so that ± 15 °, ± 45 °, and 90 ° are selected as the winding angles of the transmission shaft in the present embodiment for description.

Examples 1 to 3

Preparing the composite material transmission shaft according to the winding angle in the following winding sequence:

example 1: [ +45 °, 90 °, -45 ° ]

Example 2: [ +45 °, +15 °, -45 ° ] or [ -45 °, -15 °, +45 ° ]

Example 3: [ +15 °, +45 °, -15 ° ] or [ -15 °, -45 °, +15 ° ]

In examples 1 to 3, the thicknesses of the layers were the same, and the specific thicknesses were not limited.

In the embodiment 1, a laying mode of paired winding angles of +45 degrees and-45 degrees is adopted, and 90-degree winding angles are used for spacing between +45 degrees and-45 degrees;

example 2 on the basis that the laying mode of +45 degrees and-45 degrees paired winding angles is adopted in example 1, 90 degrees are replaced by +/-15 degrees, and the difference of the absolute values of the winding angles of adjacent layers in example 2 is smaller than that of the absolute values of the winding angles of the adjacent layers in example 1;

example 3 on the basis of example 2 without changing the winding angle, the laying order of the adjacent layers is adjusted, the winding angle ratio of +45 degrees in example 3 is 1/3, and the winding angle ratio of +45 degrees in example 2 is 2/3.

The interlaminar stress of the shaft 300 was analyzed according to the winding angles and the laying sequence of examples 1-3, and the results are shown in table 1:

TABLE 1

Categories	Stress (Mpa)
		Example 1	41.58
Example 2	55.63
		Example 3	74.46

As shown in table 1, the interlayer stress is the smallest in example 1, and it is known that the shaft body 300 has the smallest degree of deformation during operation and the most excellent torsion and compression resistance; next, examples 2 and 3, and example 3 showed the highest interlaminar stress, indicating that the shaft body 300 was deformed to the greatest extent during operation, and had the worst torsion and compression resistance.

As shown in fig. 1, one end of the shaft body 300 is connected to a driving device as a first end 301, and the other end of the shaft body 300 is connected to a transmission device as a second end 302. In this embodiment, the driving device is a wind wheel in a wind turbine generator system, and the transmission device is a gear box or a generator in the wind turbine generator system (the driving device and the transmission device are not shown in the figure).

The use of fibers can enhance the interlaminar shear strength and interlaminar tensile strength of adjacent composite layers. However, since the composite material layer is composed of fibers and resin, the shaft body 300 has heterogeneous characteristics, and has high shear and tensile strength along the fiber direction and weak shear and tensile strength away from the fiber direction, and if holes are drilled in the composite material shaft body 300, the fibers are broken or the fibers deviate from the main stress direction of the fibers, the shear resistance is relatively weak, and the connection of the driving device or the transmission device is not firm enough, which affects the connection strength. Preferably, metal parts are respectively disposed on the side walls of the shaft body 300 near the first end portion 301 and the second end portion 302 along the circumferential direction of the shaft body 300, and the metal parts are wrapped between the multiple layers of composite material layers. Meanwhile, a connecting hole 303 used for being connected with a driving device or a transmission device is formed in the end face of the shaft body 300 along the axial direction of the shaft body 300, and one side, close to the shaft body 300, of the connecting hole 303 extends along the direction close to the shaft body 300 so that part of the connecting hole 303 penetrates through the metal piece. The metal piece is made of metal material, and because the metal material is isotropic (along different directions of the shaft body 300, the periodicity and the density degree of atomic arrangement are the same, so that the physicochemical characteristics of the shaft body 300 in different directions are the same), the connecting hole 303 is arranged on the metal piece, so that the stress balance of each connecting point when the driving device or the transmission device is connected with the shaft body 300 through the connecting hole 303 and the screw can be ensured, and the connecting strength can be ensured.

In an exemplary embodiment, a mold having a cylindrical or tubular shape is prepared in advance, the composite material layer is wound by the winding apparatus according to the winding sequence of embodiment 1, and when the composite material layer is wound to a half value of the thickness of the shaft body 300 or a predetermined thickness, the composite material layer is cut at the outer sidewall of the shaft body 300 by the cutting apparatus, and the outer edge of the shaft body 300 has a polygonal shape along the radial section of the shaft body 300. Preferably, the shaft body 300 of the present embodiment has a cross section along the radial direction of the shaft body 300, and the outer edge of the shaft body 300 has a regular hexagonal shape. The metal piece with the inner ring adapted to be a regular hexagon shape is sleeved on the outer side wall, close to the first end portion 301 or the second end portion 302, of the shaft body 300, the shaft body 300 is wound by the winding device according to the winding sequence of the embodiment 1, all the metal pieces are wrapped in the multi-layer composite material layer, and finally the shaft body 300 is processed to enable the shaft body 300 to be in a radial section along the shaft body 300, and the outer edge and the inner edge of the shaft body 300 are both in a circular ring shape. The positioning structure is formed in the axial rotation direction of the metal piece along the shaft body 300 by utilizing the regular hexagonal edges of the contact side surfaces of the shaft body 300 and the metal piece, so that the metal piece and the shaft body 300 are prevented from being in a relative motion state, and the metal piece and the shaft body 300 can synchronously rotate during operation. The metal part near the first end 301 is a metal connecting flange, and the metal part near the second end 302 is a metal ring (the metal part is wrapped between composite material layers, not shown in the figure).

In order to improve the power generation operation of the wind generating set, the volume of a wind wheel (driving device) in the wind generating set is generally larger, and the diameter of a connecting shaft of the gear box (transmission device) is smaller due to the arrangement of a shell. Preferably, when finally cutting the shaft body 300 radially by using the cutting device, the outer diameter of the shaft body 300 near the first end 301 is cut larger than the outer diameter of the shaft body 300 near the second end 302. In order to ensure a uniform thickness of the shaft body 300, the inner diameter of the shaft body 300 near the first end 301 is cut by a cutting device such that the inner diameter of the shaft body 300 near the first end 301 is larger than the inner diameter of the shaft body 300 near the second end 302.

In an exemplary embodiment, the shaft body 300 is fittingly connected to a sliding bearing. The sliding bearing includes a thrust bearing 200 and a radial bearing 100. In order to ensure that the thrust bearing 200 is fittingly connected to the shaft body 300, a shoulder 304 protruding away from the shaft body 300 is provided on the outer side wall of the shaft body 300 along the circumferential direction of the shaft body 300. With the shoulder 304 as a boundary, the outer diameter of the portion of the shaft body 300 near the first end 301 of the shoulder 304 is larger than the outer diameter of the portion of the shaft body 300 near the second end 302 of the shoulder 304, and the inner diameter of the portion of the shaft body 300 near the first end 301 of the shoulder 304 is larger than the inner diameter of the portion of the shaft body 300 near the second end 302 of the shoulder 304. It should be noted that the inner and outer diameters of the shaft body 300 near the first end 301 and near the second end 302 may be set according to actual operation requirements, and are not limited to the manner in which the outer diameter and/or the inner diameter of the shaft body 300 near the first end 301 is larger than the outer diameter and/or the inner diameter of the shaft body 300 near the second end 302.

Referring to fig. 2, taking a connection flange of a wind wheel as a starting point, two radial bearings 100 for bearing radial loads and a thrust bearing 200 for bearing axial loads are sequentially mounted on a shaft body 300, wherein one radial bearing 100 (a front bearing) is mounted at a position of the shaft body 300 close to the wind wheel in a sleeved manner, the other radial bearing 100 (a rear bearing) is mounted at a first end face of the shaft body 300 close to a shaft shoulder 304 in a sleeved manner, the thrust bearing 200 is mounted on the radial bearing 100 (the rear bearing), and contact surfaces of the thrust bearing 200 and the first end face and the second end face of the shaft shoulder 304 form a sliding friction pair in actual operation. The bearing pads in the radial bearing 100 are radial pads, the bearing pads in the thrust bearing 200 are thrust pads 2, in a specific installation process, the radial pads are directly contacted with the outer circumferential surface of the shaft body 300, the thrust pads 2 are contacted with the end surface of the shaft shoulder 304, and the radial pads and the thrust pads 2 are used for bearing the radial load and the axial load of the shaft body 300.

In the installation process of the wind generating set, the radial tiles of the front bearing may be distributed at equal intervals along the circumferential direction of the shaft body 300, or may be distributed at unequal intervals. As shown in fig. 3, in order to reduce the installation cost and reduce the number of the tiles, an unequal-interval distribution mode (each triangle represents one radial tile) is adopted, the radial tiles positioned at the lower side of the shaft body 300 are used for ensuring that the shaft body 300 bears the self weight and the wind wheel weight, and meanwhile, the radial tiles positioned at the upper side of the shaft body 300 are used for bearing the shaking and deflection of the shaft body 300, so that the bouncing of the wind wheel to the shaft body 300 is reduced; the radial tiles far away from the rear bearing are arranged along the circumference of the shaft body 300 to be uniformly distributed, for example: as shown in fig. 4, each triangle represents one radial shoe, and six radial shoes are uniformly arranged along the circumferential direction of the shaft body 300. Because wind power is six-degree-of-freedom load, in order to reduce the impact load of the wind power borne by the shaft body 300, the bending load and vibration caused by the wind wheel and the influence of the vibration on the rear end of the transmission chain, the rear bearing is of an evenly distributed structure, and each radial tile can freely swing according to the changes of the rotating speed, the load and the bearing temperature to form a dynamic pressure lubricating oil film so as to support the load on the shaft body 300 and have higher stability.

As shown in fig. 5, the thrust bearing 200 includes a bearing seat 8, a fixing plate 1, and a thrust shoe 2, the bearing seat 8 is circular, the fixing plate 1 is in a fan-ring shape, and the fixing plates 1 can be spliced and installed on the end surface of the bearing seat 8 according to actual requirements to form a circular ring shape. Thrust tile 2 installs in one side that bearing frame 8 was kept away from to fixed plate 1, when thrust tile 2 damaged on fixed plate 1 or fixed plate 1, need not to carry out the whole change to thrust bearing 200, only need to damage fixed plate 1 or thrust tile 2 tear open change or maintain can, reduce thrust bearing 200 cost of maintenance and improve maintenance efficiency.

Because wind generating set operational environment is in wind gap or strong wind department usually, when actual work, axis body 300 easily receives wind wheel and wind-force influence to produce and certainly rocks or skew former installation axis, leads to axis body 300 can arouse thrust bearing 200's atress uneven when rocking or skew former installation axis, makes thrust tile 2 produce the eccentric wear, influences thrust bearing 200 and thrust tile 2 life. In this embodiment, the thrust pad 2 in the thrust bearing 200 is configured to be a tilting structure, so that when the shaft body 300 shakes or deviates from the original installation axis, the thrust pad 2 tilts through deformation of the elastic member 5 in the tilting structure to adjust its orientation to automatically adjust the load pressure, and the rigidity of an oil film is changed, thereby improving the pressure bearing capacity of the thrust pad 2 and prolonging the service life of the thrust pad 2. Preferably, the thrust pad 2 in the thrust bearing 200 may also be configured to be a non-tilting structure according to the calculated magnitude of the pressure, and the non-tilting structure will not be described in detail in this embodiment.

As shown in fig. 6 and 7, the tiltable structure may specifically be: the relative both sides of thrust tile 2 all set up spacing groove 3, set up locating part 4 on fixed plate 1, and the terminal surface that locating part 4 deviates from fixed plate 1 extends along the axial that deviates from locating part 4 and forms spacing portion 41, and spacing portion 41 is located spacing groove 3, and spacing portion 41 is the clearance setting with the lateral wall of spacing groove 3. The thrust pad 2 is mounted on the fixing plate 1 by the limiting part 41 and the limiting groove 3 in a clamping manner, and the thrust pad 2 has a certain tilting range by the gap arrangement between the limiting part 41 and the side wall of the limiting groove 3. Simultaneously, set up first recess 11 and second recess 21 respectively on fixed plate 1 and thrust tile 2 are close to the side mutually, set up elastic component 5 between first recess 11 and the second recess 21, the both ends of elastic component 5 support against in the tank bottom of first recess 11 and second recess 21 respectively, the total height of elastic component 5 is greater than the degree of depth sum of first recess 11 and second recess 21 along the degree of depth direction of first recess 11, and the outer circumferential part of elastic component 5 cooperatees with the aperture of first recess 11 and second recess 21, play coaxial and the spacing effect of circumference. In this embodiment, the limiting member 4 may be a screw, and the elastic member 5 may be made of rubber, which is not limited specifically.

When the shaft body 300 shakes or deviates from the original installation axis, pressure impact is generated on the thrust pad 2, and the elastic piece 5 generates certain deformation when the thrust pad 2 is pressed, so that the thrust pad 2 is inclined according to the deformation amount, and an oil film is formed; and the pad swings freely along with the change of the rotating speed, the load and the bearing temperature, and has better self-adaptive capacity, thereby having higher stability. Meanwhile, due to the buffering capacity of the elastic piece 5, the bearing can bear certain impact load; therefore, excessive abrasion caused by eccentric wear or impact due to uneven stress of the thrust bearing bush 2 is well avoided, and the service life of the thrust bearing bush 2 is effectively prolonged.

Preferably, be equipped with on fixed plate 1 and be circular-arc locating piece 6, locating piece 6 and thrust tile 2 deviate from axle center one side butt of fixed plate 1, and locating piece 6 plays radial spacing effect to thrust tile 2.

Preferably, the elastic member 5 is annular, so that a first oil chamber 51 is formed in the middle of the elastic member 5, the fixing plate 1 and the thrust pad 2 are respectively provided with a first oil hole 12 and a second oil hole 22, and the first oil hole 12, the first oil chamber 51 and the second oil hole 22 are communicated with each other. Meanwhile, a second oil chamber 23 is formed on the thrust pad 2 side close to the elastic member 5, and the inner diameter of the second oil chamber 23 is larger than that of the first oil chamber 51. The second oil hole 22, the second oil storage chamber 23 and the second groove 21 are concentric and communicated with each other in sequence, and a stepped hole with gradually enlarged diameter is formed. And, thrust tile 2 deviates from elastic component 5 one side and has seted up first oil groove 24, and the opening that second oilhole 22 deviates from elastic component 5 one side is located the tank bottom of first oil groove 24 to make second oilhole 22 communicate with each other with first oil groove 24, and fixed plate 1 deviates from elastic component 5 one side and has seted up second oil groove 13, and the opening that first oilhole 12 deviates from elastic component 5 one side is located the tank bottom of second oil groove 13, so that first oilhole 12 communicates with each other with second oil groove 13. And an oil inlet channel communicated with an external lubricating system is arranged on the bearing seat 8, and the oil inlet channel is communicated with the second oil groove 13. After lubricating oil sequentially passes through the oil inlet channel, the second oil groove 13, the first oil hole 12, the first oil storage chamber 51, the second oil storage chamber 23, the second oil hole 22, the first oil storage chamber 51 and the second oil storage chamber 23 through an external lubricating system, the lubricating oil is positioned between the thrust pad 2 and the shaft shoulder 304 to form a lubricating oil film, and the lubricating and bearing effects are achieved. Utilize first, second, third, second oil groove 13 to realize the memory function to lubricating oil, when the impaired unable normal leading-in lubricating oil of external lubrication system, can use the lubricating oil that exists in each oil groove to carry out the lubrication action of suspending.

Preferably, in order to reduce the mechanical wear of the contact surface of the thrust pad 2 and the shaft shoulder 304, a wear-resistant layer 7 is provided on the side of the thrust pad 2 facing away from the fixing plate 1, and the wear-resistant layer 7 may be made of a material having self-lubricating properties, such as PTFE (polytetrafluoroethylene), babbitt metal, copper alloy, etc., and is not limited herein. Combine wearing layer 7 and lubricating oil effect, effectively reduce the coefficient of rotational friction between thrust tile 2 and the axis body 300, improve thrust bearing 200 life.

The above description is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above embodiments, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention. It should be noted that modifications and embellishments within the scope of the invention may occur to those skilled in the art without departing from the principle of the invention, and are considered to be within the scope of the invention.

Claims

1. The composite material transmission shaft is characterized by comprising a shaft body, wherein the shaft body is formed by winding a plurality of composite material layers;

2. The composite drive shaft according to claim 1, wherein when the winding angle of the composite material layer is ± 45 °, the winding angle of the adjacent composite material layer is 0 ° or ± 15 ° or 90 °;

3. The composite drive shaft of claim 1 wherein said composite layers are made of a material comprising a matrix phase comprising an epoxy resin and an unsaturated polyester and a reinforcement phase comprising carbon fibers, glass fibers, aramid fibers, basalt fibers, and kenaf fibers.

4. The composite material transmission shaft according to claim 1, wherein a metal member is provided on a side wall of the shaft body near an end portion of the shaft body and in a circumferential direction of the shaft body, the metal member being wrapped between a plurality of the composite material layers;

5. The composite material transmission shaft according to claim 4, wherein a positioning structure for preventing the metal member and the shaft body from moving relatively is arranged on a contact side surface of the shaft body and the metal member.

6. The composite drive shaft according to claim 5, wherein one end portion of the shaft body is connected to a driving device as a first end portion, and the other end portion of the shaft body is connected to a transmission device as a second end portion;

7. The composite drive shaft of claim 6 wherein said shaft body has an inner diameter proximate said first end that is greater than an inner diameter of said shaft body proximate said second end.

8. The composite drive shaft according to claim 1, wherein a shoulder projecting away from the shaft body is provided on an outer side wall of the shaft body in a circumferential direction of the shaft body.

9. A plain bearing in driving fit connection with the composite material of any of claims 1 to 8, wherein the plain bearing comprises a thrust bearing and/or a radial bearing.

10. A plain bearing according to claim 9, wherein when the plain bearing is the thrust bearing, the bearing shell of the thrust bearing is in abutting engagement with the shoulder;