Double-layer film tilting pad hybrid bearing with cooling characteristic

Abstract

The invention discloses a double-layer film tilting pad hybrid bearing with a cooling characteristic, which comprises a bearing body, flexible hinges, tilting pads, axial backflow grooves, cooling pipes and throttlers, and the plurality of tilting pads are respectively connected to the bearing body through the corresponding flexible hinges; the axial backflow grooves are distributed between two adjacent tilting pads and can be communicated with gaps between the tilting pads and the bearing body; the cooling pipe is arranged on the bearing body or the tilting pad, and the inlet end of the cooling pipe is connected to an external medium supply system; a static pressure cavity is formed in the inner surface of each tilting pad, and is communicated to the cooling pipe through an inner-layer film throttler; and the cooling pipe is also communicated to a gap between the tilting pad and the bearing body through the outer layer film throttler. The bearing bush is simple in structure, can eliminate the phenomenon that the bearing bush of a traditional structure vibrates, enables bearing operation to tend to be stable, effectively reduces contact abrasion of a main shaft and the bearing bush, meanwhile, can better reduce temperature rise of an oil film in the bearing, and prolongs the service life of the bearing.

Description

Technical Field

[0001] The invention relates to the technical field of tilting pad bearing design, and in particular to a double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics. Background Art

[0002] As an indispensable basic component in mechanical equipment, the performance of the bearing will directly affect the operating efficiency of the entire transmission system. Compared with the existing fixed pad sliding bearing, the tilting pad bearing has multiple load-bearing pads, each of which can swing freely around the fulcrum independently of each other. The tilting pad sliding bearing has a larger degree of freedom, a smaller bearing cross stiffness, a significant damping effect, and higher stability. It has high stability and load-bearing capacity, so that it can be applied to more work scenarios. However, as a kind of hydrodynamic bearing, the traditional tilting pad bearing will inevitably cause contact wear between the main shaft and the bearing due to the low speed and low oil film pressure in the bearing during the initial stage of spindle startup, which reduces the lubrication performance and service life of the bearing, thereby affecting the normal operation of the bearing. Therefore, in order to overcome the design defects of the traditional tilting pad, its structure needs to be improved.

[0003] As the requirements for bearing speeds become higher and higher, the temperature rise of lubricating oil becomes more and more serious. The high-speed rotating journal drives the lubricating oil to move in the bearing, and the friction between the oil film molecules will generate excessive heat, which will increase the temperature of the oil film. The increased temperature will reduce the viscosity of the lubricating oil, affecting the lubrication performance of the bearing, and even causing the oil film to rupture, increasing the degree of bearing wear and causing major safety accidents. Summary of the invention

[0004] The purpose of the present invention is to solve the shortcomings of the above-mentioned existing background technology and to provide a double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics to solve the problem of contact wear of the existing tilting pad bearing and the problem of decreased bearing lubrication performance due to increased lubricating oil temperature during high-speed rotation.

[0005] In order to solve the above technical problems, the technical solution adopted by the present invention is: a double-layer diaphragm tilting pad dynamic and static pressure bearing with cooling characteristics, including a bearing body, a flexible hinge, a tilting pad, an axial reflow groove, a cooling pipe and a throttle, a plurality of the tilting pads are connected and embedded in the inner ring of the bearing body through corresponding flexible hinges, and are arranged at equal intervals along its circumferential direction, a plurality of axial reflow grooves are respectively arranged between two adjacent tilting pads, and their protruding height relative to the bearing body is less than the installation height of the tilting pad, and can be connected with the gap between the tilting pad and the bearing body; the cooling pipe is arranged on the bearing body or the tilting pad, and its inlet end is connected to an external medium supply system; the inner surface of each tilting pad is provided with a static pressure cavity, which is connected to the above cooling pipe through the inner diaphragm throttle; the cooling pipe is also connected to the gap between the above tilting pad and the bearing body through the outer diaphragm throttle.

[0006] Furthermore, each tilting pad is connected to the bearing body via a deformable flexible hinge, and the bearing body, the flexible hinge and the tilting pad are an integrally formed structure and are made of the same material.

[0007] Furthermore, the cooling pipe is arranged on the bearing body, and a detachable outer ring bearing is installed on the outer side of the bearing body. The cooling pipe is divided into two parts and is symmetrically arranged on the outer surface of the bearing body and the inner surface of the outer ring bearing, and the two are tightly fitted.

[0008] Furthermore, the inner film throttle penetrates and connects the center position of the tilting pad, the center position of the flexible hinge and the bearing body, so that the static pressure cavity is connected to the cooling pipe; each tilting pad corresponds to two outer film throttles, which are respectively located on both sides of a single set of inner flexible hinges.

[0009] Furthermore, there are three tilting pads arranged equidistantly around the circumference, including a left pad, a lower pad and a right pad, whose width is consistent with the width of the bearing body. The wrap angle of each tilting pad is 100°, and the center of each tilting pad is located at 60°, 180° and 300° of the bearing in a clockwise direction.

[0010] Furthermore, the static pressure cavity is opened at the center of each tilting pad, and its circumferential length accounts for 30% of the tilting pad, the axial length accounts for 40% of the width of the tilting pad, and the total area accounts for 12% of the inner surface area of ​​the tilting pad.

[0011] Furthermore, the static pressure chamber is rectangular, or elliptical, or rounded rectangular.

[0012] Furthermore, there are three axial return grooves, including an upper return groove, a left return groove and a right return groove. The circumferential wrap angle of each axial return groove is 20°, and the center of each axial return groove is located at 0°, 120°, and 240° directions of the bearing in a clockwise direction.

[0013] Furthermore, there are three cooling pipes, and their layout paths are all M-shaped, H-shaped, or N-shaped. The tail end of each cooling pipe corresponds to a flexible hinge; the same medium, oil or water, is injected into each cooling pipe.

[0014] Furthermore, the inner membrane throttle and the outer membrane throttle are both capillary throttles, or small hole throttles, film throttles, and slide valve throttles.

[0015] Compared with the prior art, the present invention has the following beneficial effects:

[0016] 1) In the present invention, the bearing body, flexible hinge and tilting pad are an integrated formed structure, which reduces the difficulty of processing and assembly, and has the advantages of no bearing vibration and error accumulation; at the same time, a deformable flexible hinge is used to replace the traditional rigid fulcrum, which has the advantages of reducing processing and manufacturing costs, no high contact stress and fulcrum wear, and at the same time eliminates the bearing vibration caused by the non-load-bearing pad of the traditional structure, so that the bearing operation is more stable and the service life of the bearing is increased.

[0017] 2) In the present invention, the inner surface of the tilting pad is divided into a static pressure cavity and an oil sealing surface, wherein the film pressure on the oil sealing surface is a dynamic pressure, which is mainly derived from the fluid dynamic pressure effect caused by the mutual squeezing of medium film molecules when the lubricating medium flows in the bearing. The dynamic pressure principle is utilized to overcome the problems of spindle drift and insufficient oil film rigidity of the static pressure bearing; the film pressure in the static pressure cavity is a static pressure, and a high-pressure medium is injected into the static pressure cavity through a throttle to support the spindle and make it suspended. The static pressure principle is utilized to overcome the problem of contact wear between the spindle and the bearing of the dynamic pressure bearing.

[0018] 3) The present invention has a simple structure, and a detachable outer ring bearing is provided on the outer side of the bearing body, and cooling pipes of different shapes are processed between the two. The setting of the cooling pipe can make the cooling range larger, have a better cooling effect on the inside of the bearing, and reduce the temperature rise of the oil film. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a schematic diagram of the overall structure of the present invention;

[0020] Figure 2 An exploded view of one of the outer ring bearings compared to the bearing body in the present invention;

[0021] Figure 3 A front view of the layout of one of the cooling pipes in the present invention;

[0022] Figure 4 for Figure 3 Sectional view in the AA direction;

[0023] Figure 5It is a diagram showing the inner surface of the outer ring bearing in the present invention;

[0024] Figure 6 is the dimensionless temperature distribution diagram at the axial mid-section of the bearing;

[0025] Figure 7 is the dimensionless temperature distribution diagram at the mid-section of the bearing circumference;

[0026] Figure 8 It is the bearing force analysis diagram;

[0027] Fig. 9 This is the pressure diagram of the inner axial mid-section of the bearing when the double-layer oil film effect is not considered;

[0028] Fig.10 It is the pressure distribution diagram of the axial mid-section of the inner layer of the bearing when the double-layer oil film effect is considered;

[0029] Fig.11 This is the diagram of the change in the outer oil film pressure of the bearing when the double-layer oil film effect is considered;

[0030] In the figure: 1, bearing body, 2, flexible hinge, 3, tilting pad, 4, axial return groove, 5, static pressure chamber, 6, outer ring bearing, 7, cooling pipe, 8, inner film throttle, 9, outer film throttle, 10, medium inlet end, 11, outer gap. DETAILED DESCRIPTION

[0031] It should be noted that, in the description of the present invention, terms such as "upper", "lower", "left", "right", "circumferential", "axial", "inner", "outer", "front", "rear", "one end", "the other end" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are relational words determined only for the convenience of describing the structural relationships of the various components in the present invention, and do not specifically mean that any component in the present invention must have a specific orientation, be constructed and operated in a specific orientation, and should not be understood as a limitation on the present invention.

[0032] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings:

[0033] Embodiment 1,

[0034] like Figures 1 to 5As shown, a double-layer membrane tilting pad dynamic and static pressure bearing with cooling characteristics includes a bearing body 1, a flexible hinge 2, a tilting pad 3, an axial reflow groove 4, a cooling pipe 7 and a plurality of different throttles, wherein three tilting pads 3 are provided, each of which corresponds to a flexible hinge 2, and the tilting pad 3 is connected to the inner ring of the bearing body 1 through the flexible hinge 2, and an axial reflow groove 4 is provided in the inner ring of the bearing body 1 between each two adjacent tilting pads 3; the above-mentioned bearing body 1, flexible hinge 2, and tilting pad 3 are integrally processed to form a structure, using the same material and processed by electric spark wire cutting, and the error can be controlled within ±2 microns to meet the processing accuracy requirements of the circular arc surface of the pad, while reducing the difficulty of processing and assembly; the above-mentioned flexible hinge 2 can be deformed, replacing the traditional rigid fulcrum, so that the bearing operation tends to be more stable, especially in a high-speed rotor system, the advantages of the flexible fulcrum tilting pad bearing are more significant.

[0035] The above three tilting pads 3 are arranged equidistantly along the circumferential direction of the bearing body 1, including a left pad, a lower pad and a right pad. The width of the pads is consistent with the width of the bearing body 1. The wrap angle of each tilting pad 3 is 100°. In the clockwise direction, the center of each tilting pad 3 is located at 60°, 180° and 300° directions of the bearing respectively. A static pressure cavity 5 is provided at the center of the inner surface of each tilting pad 3, and its processed shape is rectangular. The main function of the static pressure cavity 5 is to ensure that the supporting force of the static pressure cavity 5 is sufficient to separate the main shaft and the tilting pad 3 when the medium is fully supplied before the main shaft is started. As the main shaft speed increases, the dynamic pressure effect in the bearing is continuously strengthened. At this time, dynamic pressure support is mainly adopted. Therefore, in the process of processing the static pressure cavity 5, it is required that the area of ​​the inner surface of the tilting pad 3 occupied by the static pressure cavity 5 should not be too large, otherwise the static pressure inside it will affect the formation of dynamic pressure. Therefore, the circumferential length of the static pressure cavity 5 (in the direction of the circumferential length of the bearing) accounts for 30% of the tilting pad 3, and its axial length (in the direction of the axial length of the bearing) accounts for 40% of the tilting pad 3, and the overall area accounts for 12% of the tilting pad 3; the inner surface of the tilting pad 3 excluding the static pressure cavity part is the oil sealing surface, and the medium film pressure thereon is the dynamic pressure. The processing area of ​​the static pressure chamber 5 can also be set according to actual application requirements, and the maximum area cannot exceed the area of ​​the entire tilting pad 3, and the minimum area cannot be less than the area of ​​the throttle inlet.

[0036] The tilting pad 3 and the bearing body 1 are arranged in an overhead structure, and an outer layer gap 11 is left between the two; an integrated axial return groove 4 is fixedly provided on the inner side of the bearing body between each two adjacent tilting pads 3, and there are three in total, including an upper return groove, a left return groove and a right return groove. The circumferential wrap angle of each axial return groove 4 is 20°, and the center of each axial return groove 4 is located at 0°, 120°, and 240° directions of the bearing in a clockwise direction, and the protruding height of each axial return groove 4 compared to the inner ring of the bearing body is smaller than the installation height of the tilting pad 3, so that it can be connected with the above-mentioned outer layer gap 11, thereby ensuring the return path of the medium and realizing recycling. The outer side surface of the bearing body 1 is also provided with a detachable and fixed outer ring bearing 6 around it, specifically including three outer ring bearings 6 arranged in sequence, each outer ring bearing 6 is fixed to the bearing body 1 by countersunk screws passing through its four corners, and the center point of each outer ring bearing 6 corresponds to the center of a single axial return groove 4, and the outer ring bearings 6 are tightly fitted to the bearing body 1, and a cooling pipe 7 with an M-shaped path is arranged between the two (the path shape of the cooling pipe 7 can also be H-shaped, N-shaped, trapezoidal, etc., and it is arranged according to actual production needs. The cooling performance of different cooling pipe paths will be different), the cooling range is larger, in order to make the processing technology of the cooling pipe 7 simpler The cooling pipe 7 is divided into two parts, which are symmetrically arranged on the inner surface of the outer ring bearing 6 and the outer surface of the bearing body 1. One end of the overall cooling pipe 7 extends to the outside to form a medium inlet end 10, and the other end is buried inside between the outer ring bearing 6 and the bearing body 1, located just above the flexible hinge 2, and passes through the bearing body 1, the center position of the flexible hinge 2, and the tilting pad 3 in sequence through the inner film throttle 8 to be connected to the corresponding static pressure cavity 5; two through holes are also arranged in the cooling pipe 7, each of which is interference-fitted with an outer film throttle 9, which are respectively connected to the outer layer gap 11 between the two adjacent tilting pads 3 and the bearing body 1 located on both sides of the single axial reflux groove 4.

[0037] The inner film throttle 8 and the outer film throttle 9 are both capillary throttles, which are pressure automatic compensation adjustment elements. When the lubricating medium flows through the throttle, the pressure of each oil chamber can be automatically adjusted to adapt to the changes of different external loads. Alternatively, one of a small hole throttle, a film throttle, and a slide valve throttle can be selected.

[0038] There are three cooling pipes 7 , which are respectively located on the inner sides of the three outer ring bearings 6 , and the medium inlet ends 10 thereof are connected to the external medium supply system, and the same medium, such as oil, is injected into the interior thereof.

[0039] In specific use, when the spindle starts, due to its low speed, the dynamic pressure generated is not enough to support the entire shaft system. At this time, it mainly relies on static pressure support, such as Figure 8As shown. The oil is injected into the cooling pipe 7 through the medium inlet end 10 by a hydraulic pump, and then enters the static pressure chamber 5 through the inner film throttle 8 to form a high-pressure oil film, so that the main shaft and the tilting pad 3 are separated and suspended in the bearing. At this time, the lubricating oil is mostly low-temperature lubricating oil. As the main shaft speed continues to increase, the tilting pad 3 swings under the action of the oil film, so that the wedge effect in the bearing continues to increase, and the dynamic pressure in the bearing increases accordingly. When the dynamic pressure on the inner surface of the tilting pad 3 is much greater than the static pressure in the static pressure chamber 5, the bearing at this time mainly adopts dynamic pressure support.

[0040] As the spindle speed increases, the oil film bearing capacity and friction force also increase. In this process, the friction force continuously generates a large amount of heat, which increases the temperature of the lubricating oil. During the rotation process, low-temperature lubricating oil is always injected into the cooling pipe 7 so that the temperature of the bearing body is consistent with the temperature of the low-temperature lubricating oil. When the hot lubricating oil flows through the cooling pipe 7, heat is transferred, which reduces the temperature of the hot lubricating oil.

[0041] As the spindle speed increases, the lubricating oil flows rapidly in the bearing gap. Part of the lubricating oil always flows on the oil sealing surface of the tilting pad 3, while the other part of the lubricating oil flows into the back of the tilting pad 3 through the gap of the axial return groove 4. When the speed reaches a certain value, the dynamic pressure on the oil sealing surface will cause the flexible hinge 2 to deform slightly, causing the tilting pad 3 to swing. When the tilting pad 3 swings, it will squeeze the lubricating oil on the back. At this time, the lubricating oil on the back will generate a reaction force to hinder the swing of the tilting pad 3; at the same time, the lubricating oil is also injected into the outer gap 11 through the inner and outer film throttles 9 of the cooling tube 7 to form a reaction force together. Under the action of the oil film pressure of the double-layer oil film on the oil sealing surface and the back of the pad, the tilting pad 3 continuously adjusts itself and finally reaches a state of equilibrium without swinging. Please refer to Figure 8 Bearing force analysis diagram is shown.

[0042] In order to study the change of oil film pressure in the static pressure cavity 5 of each pad, the pressure of the axial mid-section of the bearing is cut as follows: Fig. 9As shown. When the preload coefficient increases from 0.1 to 0.4, the oil film pressure in the left bearing static pressure chamber 5 increases from 0.6813 to 0.8829, an increase of 29.58%; the oil film pressure in the lower bearing static pressure chamber 5 increases from 0.9899 to 1.1564, an increase of 16.81%; the oil film pressure in the right bearing static pressure chamber 5 increases from 0.6986 to 0.8927, an increase of 27.79%. This is because the smaller the preload coefficient, the greater the distance between the bearing and the shaft, and the weaker the fluid dynamic pressure effect in the bearing, so that the dynamic pressure on the sealing oil surface is less than the static pressure in the static pressure oil chamber. At this time, the main shaft mainly relies on static pressure support, such as when the preload coefficient m=0.1. As the preload coefficient increases, the distance between the pad and the rotating shaft gradually decreases, the wedge effect gradually increases, and the fluid dynamic pressure increases. When the dynamic pressure on the oil sealing surface is much greater than the static pressure in the static pressure chamber 5, the main shaft mainly relies on dynamic pressure support, such as when the preload coefficient m=0.4.

[0043] Fig.11 The variation of dimensionless outer oil film pressure with preload coefficient after considering double oil film effect is given. It can be seen that with the increase of preload coefficient, the outer oil film pressure of each pad shows a trend of gradual increase. When the preload coefficient m=0.1, the dimensionless maximum outer oil film pressure of the left pad, lower pad and right pad are 0.1817, 0.9978 and 0.6339 respectively; when the preload coefficient m=0.4, the dimensionless maximum outer oil film pressure of the left pad, lower pad and right pad are 0.3254, 1.3290 and 0.9858 respectively, which increase by 79.09%, 33.19% and 55.52% respectively. This is because when the preload coefficient increases, the wedge effect between each pad and the shaft is enhanced, and the inner oil film pressure shows a trend of gradual increase, which makes the pad swing angle larger, thereby enhancing the squeezing effect of the pad on the outer oil film, so that the outer oil film pressure of each pad gradually increases.

[0044] Fig.10This is the pressure distribution diagram of the axial mid-section of the bearing after considering the double-layer oil film effect. Regardless of whether the double-layer oil film effect is considered, the overall change trend of the oil film pressure with the preload coefficient is consistent. The inner and outer oil film pressures of each bearing pad always increase with the increase of the preload coefficient. The difference is that after considering the double-layer oil film effect, the values ​​of the oil film pressures of each part will be significantly reduced. For example, when the preload coefficient increases from 0.1 to 0.4, the oil film pressure in the static pressure cavity 5 of the left pad increases from 0.6359 to 0.8280, an increase of 30.21%; the oil film pressure in the static pressure cavity 5 of the lower pad increases from 0.9756 to 1.1474, an increase of 17.62%; the oil film pressure in the static pressure cavity 5 of the right pad increases from 0.6513 to 0.84521, an increase of 29.77%. This is because the existence of the outer oil film pressure inhibits the dynamic pressure effect of the inner fluid. Specifically, as the preload coefficient increases, the distance between the pad and the shaft decreases, the wedge effect between the pad and the shaft increases, and the pad swing angle swings to a large extent. The outer oil film is squeezed by the pad, which hinders the swing of each pad, weakening the dynamic pressure effect of the inner oil film pressure and reducing the oil film pressure.

[0045] Embodiment 2,

[0046] A double-layer membrane tilting pad dynamic and static pressure bearing with cooling characteristics, comprising a bearing body 1, a flexible hinge 2, a tilting pad 3, an axial reflux groove 4, a cooling pipe 7 and a plurality of different throttles, the overall structure of which is similar to the technical solution described in the above-mentioned embodiment 1, the difference between the two is that the cooling pipe 7 is arranged inside the tilting pad 3, and can be arranged in a straight line or a paper clip path to cool the oil sealing surface of the inner surface of the tilting pad 3, referring to Figure 6 and Figure 7 As shown, it can be seen that after the cooling tube 7 is processed on the bearing, the cooling contact distance is closer and the temperature of the bearing drops significantly.

[0047] Embodiment 3,

[0048] A double-layer diaphragm tilting pad hydrostatic bearing with cooling characteristics comprises a bearing body 1, a flexible hinge 2, a tilting pad 3, an axial reflux groove 4, a cooling pipe 7 and a plurality of different throttles. The overall structural arrangement is similar to the technical scheme described in the above-mentioned embodiment 1. The difference between the two is that the static pressure cavity 5 opened on the inner surface of the tilting pad 3 is elliptical or rounded rectangular.

[0049] Embodiment 4,

[0050] A double-layer diaphragm tilting pad dynamic and static pressure bearing with cooling characteristics includes a bearing body 1, a flexible hinge 2, a tilting pad block 3, an axial reflux groove 4, a cooling pipe 7 and a plurality of different throttles. Its overall structural arrangement is similar to the technical scheme described in the above-mentioned embodiment 1. The difference between the two is that the same medium is injected into each cooling pipe 7, which can be water.

[0051] In addition, the above-mentioned tilting pads 3 can be provided in various different quantities such as four or five, and the corresponding number of flexible hinges 2 is the same; at the same time, the size and position angle of the tilting pads 3 are adjusted accordingly to adapt to the adjustment application in the actual processing scenario, and the static pressure cavity 5 set on the inner side can also be adjusted according to actual processing requirements.

[0052] In the above description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "install", "connect", "connect", "open", etc. should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0053] Of course, the above description is not a limitation of the present invention, and the present invention is not limited to the above examples. Changes, modifications, additions or substitutions made by technicians in this technical field within the essential scope of the present invention should also fall within the protection scope of the present invention.

Claims

1. A double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics, characterized in that: It includes a bearing body, a flexible hinge, a tilting pad, an axial reflow groove, a cooling pipe and a throttle. A plurality of the tilting pads are connected and embedded in the inner ring of the bearing body through corresponding flexible hinges and are arranged at equal intervals along the circumferential direction. A plurality of axial reflow grooves are respectively arranged between two adjacent tilting pads, and their protruding height relative to the bearing body is less than the installation height of the tilting pad, and can be connected with the gap between the tilting pad and the bearing body; the cooling pipe is arranged on the bearing body or the tilting pad, and its inlet end is connected to the external medium supply system; a static pressure cavity is provided on the inner surface of each tilting pad, which is connected to the cooling pipe through an inner film throttle; the cooling pipe is also connected to the gap between the tilting pad and the bearing body through an outer film throttle.

2. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 1, characterized in that: Each tilting pad is connected to the bearing body via a deformable flexible hinge. The bearing body, the flexible hinge and the tilting pad are an integrally formed structure and are made of the same material.

3. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 2, characterized in that: The cooling pipe is arranged on the bearing body, and a detachable outer ring bearing is installed on the outer side of the bearing body. The cooling pipe is divided into two parts, which are symmetrically arranged on the outer surface of the bearing body and the inner surface of the outer ring bearing, and the two are tightly fitted.

4. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 3, characterized in that: The inner film throttle penetrates and connects the center position of the tilting pad, the center position of the flexible hinge and the bearing body, so that the static pressure cavity is connected with the cooling pipe; each tilting pad corresponds to two outer film throttles, which are respectively located on both sides of a single set of inner flexible hinges.

5. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 1, characterized in that: There are three tilting pads arranged equidistantly around the circumference, including a left pad, a lower pad and a right pad. Their widths are consistent with the width of the bearing body. The wrap angle of each tilting pad is 100°. In the clockwise direction, the center of each tilting pad is located at 60°, 180° and 300° of the bearing respectively.

6. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 5, characterized in that: The static pressure cavity is opened at the center of each tilting pad, and its circumferential length accounts for 30% of the tilting pad, the axial length accounts for 40% of the width of the tilting pad, and the total area accounts for 12% of the inner surface area of ​​the tilting pad.

7. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 5, characterized in that: The static pressure chamber is rectangular, elliptical, or rounded rectangular.

8. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 5, characterized in that: There are three axial return grooves, including an upper return groove, a left return groove and a right return groove. The circumferential wrap angle of each axial return groove is 20°, and the center of each axial return groove is located at 0°, 120°, and 240° directions of the bearing in a clockwise direction.

9. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 5, characterized in that: There are three cooling pipes, and the layout paths are all M-shaped, H-shaped, or N-shaped. The tail end of each cooling pipe corresponds to a flexible hinge; the same medium, oil or water, is injected into each cooling pipe.

10. The double-layer film tilting pad dynamic and static pressure bearing with cooling characteristics according to claim 1, characterized in that: The inner membrane throttle and the outer membrane throttle are both capillary throttles, or small hole throttles, film throttles, and slide valve throttles.

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