Ball bearing with spiral cooling structure and bearing cooling and lubricating method

Abstract

The invention relates to the technical field of aero-engine bearing cooling, in particular to a ball bearing with a spiral cooling structure and a bearing cooling and lubricating method. Which comprises a bearing inner ring, a bearing outer ring and a retainer which are coaxially arranged in the bearing, and a plurality of balls which are circumferentially distributed on the retainer, and is characterized in that a spiral cooling runner is arranged in the bearing outer ring, and the spiral cooling runner takes the axis where the center of the bearing is located as the axis of a spiral line; a cooling lubricating oil inlet and a cooling lubricating oil outlet which are communicated with the spiral cooling flow channel are further formed in the bearing outer ring, and an inner ring oil supply hole for supplying oil to the balls is formed in the bearing inner ring in a penetrating mode. Through the spiral cooling flow channel arranged in the bearing, independent cooling and heat exchange of the outer ring of the ball bearing can be achieved, the viscous friction loss of lubricating oil in a bearing cavity is reduced, efficient cooling of the interior of the bearing is achieved, and the service life of the bearing is prolonged.

Description

Technical Field

[0001] The invention relates to the technical field of cooling of aircraft engine bearings, and in particular to a ball bearing with a spiral cooling structure and a bearing cooling and lubricating method. Background Art

[0002] High-speed rolling bearings in aircraft engines require lubrication and cooling with lubricating oil. In actual operation, only a very small amount of lubricating oil inside the bearing will enter the contact area to form a lubricating oil film, and most of the other lubricating oil is mainly used for cooling, and the heat generated by the bearing is carried away through convection heat transfer.

[0003] At present, the existing bearing cooling methods have developed from traditional single jet lubrication to under-ring lubrication or under-ring / jet combined lubrication. Both cooling methods are "lubricating oil outflow cooling", where the lubricating oil flows through the surface of the bearing parts and cools the bearings through convective heat transfer. Among them, under-ring lubrication is a lubrication method that sends lubricating oil into the bearing through the oil supply hole of the inner ring of the bearing. Compared with jet lubrication, under-ring lubrication has better lubrication and cooling effects. However, both under-ring lubrication and jet lubrication will cause large-scale retention of lubricating oil liquid in the bearing cavity. When the rolling element runs at high speed in this oil environment, it will produce significant fluid viscous friction such as oil stirring and dragging, which will increase the heat generation of the bearing and increase the cooling and heat transfer load. As advanced engines develop towards high intake temperature and high turbine pre-gas temperature, the ultra-high temperature and gas environment faced by bearings have seriously exceeded the current tolerance; at the same time, the variable operating conditions of variable cycle engines, the improvement of thrust-to-weight ratio, and the control of rotor vibration require the development of revolutionary new bearing structures and cooling solutions.

[0004] In response to the above situation, Germany's MTU Engine Company has developed an "external ring cooling technology". The lubricating oil that enters the bearing through the oil supply hole under the ring is mainly used to meet the cooling and lubrication of the inner ring and rolling elements. The outer ring cooling is completed by the oil supply channel surrounded by the outer diameter surface of the outer ring. This part of the lubricating oil does not enter the inside of the bearing, so the lubricating oil flow entering the bearing can be appropriately reduced, thereby reducing the fluid viscous friction loss of the bearing. However, the defect of this technology is that the lubricating oil groove for the separate cooling of the outer ring is arranged on the outer diameter surface of the outer ring, resulting in the inability to effectively control the bearing structure temperature. At the same time, the bearing fluid viscous friction loss is high, that is, the bearing cooling and lubrication effect is not ideal. The invention patent "A ball bearing with a cooling structure and a bearing cooling and lubrication method" (patent number CN202210177014.5) discloses a ball bearing with a cooling structure and a bearing cooling and lubrication method. The ball bearing includes a ball bearing inner ring, a retaining frame and a ball bearing outer ring arranged in sequence from the inside to the outside. The interior of the ball bearing outer ring is provided with a multi-channel annular cooling flow channel. During the research process, the temperature of the structure is relatively high. The spiral cooling structure proposed in the present invention has better cooling performance than the multi-channel structure. Specifically, the maximum temperature of the fluid domain, i.e., the lubricating oil, and the maximum temperature of the solid domain, i.e., the outer ring of the bearing have been reduced. Under given working conditions, the maximum temperature of the fluid domain of the spiral cooling structure has dropped by 15.5%, and the maximum temperature of the solid domain has dropped by 2.2%. Summary of the invention

[0005] The purpose of the present invention is to avoid the shortcomings of the prior art and to provide a ball bearing with a spiral cooling structure and a bearing cooling and lubrication method, which solves the technical problem that the bearing cooling and lubrication effect in the prior art is not ideal by setting a spiral cooling channel inside the bearing outer ring.

[0006] To achieve the above-mentioned purpose, the technical solution adopted by the present invention is as follows: the ball bearing with a spiral cooling structure comprises a bearing inner ring, a bearing outer ring, a retaining frame and a plurality of balls arranged circumferentially on the retaining frame coaxially arranged in the bearing, the interior of the bearing outer ring is provided with a spiral cooling channel, and the spiral cooling channel has the axis at the center of the bearing as the spiral axis; the interior of the bearing outer ring is also provided with a cooling lubricating oil inlet and a cooling lubricating oil outlet connected to the spiral cooling channel, and the inner ring of the bearing is provided with an inner ring oil supply hole for supplying oil to the balls.

[0007] The flow channels of the cooling and lubricating oil inlet and the cooling and lubricating oil outlet are both arranged parallel to the bearing axis direction; the flow channel cross-sections of the cooling and lubricating oil inlet and the cooling and lubricating oil outlet are circular cross-sections; the cross-section of the spiral cooling flow channel is a circular cross-section, the spiral cooling flow channel is tangent to the flow channels of the cooling and lubricating oil inlet and the cooling and lubricating oil outlet, and the cross-section circle diameters of the spiral cooling flow channel, the cooling and lubricating oil inlet and the cooling and lubricating oil outlet are all d.

[0008] The flow channel of the cooling lubricating oil inlet and the flow channel of the cooling lubricating oil outlet are placed on different sides of the outer ring of the ball bearing. The flow channels of the cooling lubricating oil inlet and the cooling lubricating oil outlet are both b in length and are centrally symmetrically distributed relative to the outer ring of the bearing.

[0009] The spiral cooling channel starts from the end of the channel at the cooling lubricating oil inlet and ends at the beginning of the channel at the cooling lubricating oil outlet. The number of spiral turns is n. Starting from the starting point of the spiral cooling channel, the pitch of the first turn is a1, the pitch of the second turn is a2, and the pitch of the nth turn is a n , when a1=a2=…=a n When the spiral cooling channel is a spiral line with equal pitch, the height of the spiral line is , in a1, a2, ..., a n When the pitch is not completely equal, the spiral cooling channel is a non-uniform helix. The width W of the bearing outer ring, the height h of the helix, and the length b of the flow channel of the cooling lubricating oil inlet satisfy the equation: .

[0010] The center line of the spiral cooling channel is tangent to a line, and the tangent is a straight line or an arc with the center of curvature of the outer ring channel as the center. When the tangent is a straight line, the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel is the vertical distance between the straight line and the center of curvature of the outer ring channel; when the tangent is an arc, the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel is the radius of the arc.

[0011] The radius r of the outer ring channel, the distance c between the tangent line of the spiral cooling channel centerline and the center of curvature of the outer ring channel, and the diameter d of the cooling channel cross section circle satisfy the inequality relationship: .

[0012] The value range of the width W of the bearing outer ring is [8d, 12d], the value range of the thickness T of the bearing outer ring is [2d, 8d], the value range of the outer diameter of the bearing outer ring is [45d, 53d], the value range of the groove bottom diameter of the bearing outer ring is [42d, 48d], the value range of the inner diameter of the bearing outer ring is [40d, 48d], the value range of the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel of the center line of the spiral cooling channel is [6d, 8d], and the value range of the radius r of the bearing outer ring channel is [5d, 6d].

[0013] A method for cooling and lubricating a bearing with a spiral cooling structure is characterized in that cooling and lubricating oil is introduced into an outer ring of the bearing with a spiral cooling structure to achieve cooling and lubrication, and specifically comprises the following steps: Step 1: The cooling lubricating oil is passed through the cooling lubricating oil inlet on one side of the bearing outer ring and into the spiral cooling flow channel through the cooling lubricating oil inlet flow channel. The cooling lubricating oil entering the spiral cooling flow channel finally flows out from the cooling lubricating oil outlet flow channel on the other side of the bearing outer ring, thereby completing the cooling of the bearing outer ring. Step 2: Pass the cooling lubricating oil into the bearing with a spiral cooling structure through the inner ring oil supply hole. The cooling lubricating oil flows through the bearing inner ring, retaining frame and balls to complete the cooling and lubrication of the bearing inner ring, retaining frame and balls.

[0014] The initial temperature of the cooling lubricating oil is 300K-350K, and the heat flux density is 100000W / m 2 ~200000W / m 2 , the oil supply flow rate is 0.5L / min~3L / min.

[0015] The initial temperature of the cooling lubricating oil is 323.15K, and the heat flux density is 150000W / m 2 , the oil supply flow rate is 2.5L / min.

[0016] Compared with the prior art, the present invention has the following technical effects: a ball bearing and a bearing cooling and lubrication method with a spiral cooling structure, which can realize separate cooling and heat exchange of the outer ring of the ball bearing through the spiral cooling flow channel arranged inside, thereby improving the situation that the traditional cooling scheme does not cool the outer ring of the ball bearing enough, and then reducing the amount of sprayed cooling lubricating oil, reducing the viscous friction loss of the lubricating oil in the bearing cavity, realizing efficient cooling inside the bearing, and improving the service life of the bearing. At the same time, the spiral cooling structure of the present invention includes a cooling lubricating oil inlet flow channel parallel to the axial direction, a spiral cooling flow channel with the axis of the bearing center as the spiral axis, and a cooling lubricating oil outlet flow channel parallel to the axial direction. The flow channel is long, the heat exchange area between the cooling lubricating oil and the outer ring of the bearing is large, and the cooling effect is good. Compared with the prior art, it can reduce the maximum temperature of the cooling lubricating oil and the maximum temperature of the outer ring of the bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 An axial cross-sectional view of a ball bearing with a spiral cooling structure according to the present invention; Figure 2 is a radial cross-sectional view of a ball bearing with a spiral cooling structure according to the present invention; Figure 3 For the present invention Figure 2 Radial section view of the outer ring of the middle bearing; Figure 4 For the present invention Figure 3 An enlarged schematic diagram of the local structure of the bearing outer ring; Figure 5It is a schematic diagram of the structure of the spiral cooling channel of the present invention; Figure 6 It is a schematic structural diagram of the outer ring of the ball bearing of the present invention.

[0018] In the figure, 1, bearing; 101, bearing inner ring; 102, retaining frame; 103, bearing outer ring; 104, ball; 105, inner ring oil supply hole; 106, spiral cooling channel; 107, cooling lubricating oil inlet; 108, cooling lubricating oil outlet. DETAILED DESCRIPTION

[0019] The principles and features of the present invention are described below in conjunction with the accompanying drawings; the examples given are only used to explain the present invention; they are not used to limit the scope of the present invention.

[0020] In order to achieve the above object, the present invention provides the following specific implementation methods: Figure 1 , 2 As shown in Figures 5 and 6, a ball bearing with a spiral cooling structure includes a bearing inner ring 101, a bearing outer ring 103, a retaining frame 102 and a plurality of balls 104 arranged circumferentially on the retaining frame 102 coaxially arranged in the bearing 1, and is characterized in that a spiral cooling channel 106 is arranged inside the bearing outer ring 103, and the spiral cooling channel 106 takes the axis at the center of the bearing 1 as the spiral axis; the bearing outer ring 103 is also provided with a cooling lubricating oil inlet 107 and a cooling lubricating oil outlet 108 connected to the spiral cooling channel 106, and the bearing inner ring 101 is provided with an inner ring oil supply hole 105 for supplying oil to the balls 104.

[0021] like Figure 3 and 4 As shown, the flow channels of the cooling lubricating oil inlet 107 and the cooling lubricating oil outlet 108 are arranged parallel to the bearing axis direction; the flow channel cross-sections of the cooling lubricating oil inlet 107 and the cooling lubricating oil outlet 108 are circular cross-sections; the cross-section of the spiral cooling flow channel 106 is a circular cross-section, the spiral cooling flow channel 106 is tangent to the flow channels of the cooling lubricating oil inlet 107 and the cooling lubricating oil outlet 108, and the flow channel cross-section circle diameters of the spiral cooling flow channel 106, the cooling lubricating oil inlet 107 and the cooling lubricating oil outlet 108 are all d.

[0022] The flow channel of the cooling lubricating oil inlet 107 and the flow channel of the cooling lubricating oil outlet 108 are placed on different sides of the outer ring of the ball bearing. The flow channel lengths of the cooling lubricating oil inlet 107 and the cooling lubricating oil outlet 108 are both b, and are centrally symmetrically distributed relative to the outer ring of the bearing.

[0023] The spiral cooling channel 106 starts from the end of the cooling lubricating oil inlet 107 and ends at the beginning of the cooling lubricating oil outlet 108. The number of spiral turns is n. Starting from the starting point of the spiral cooling channel, the first turn pitch is a1, the second turn pitch is a2, and the nth turn pitch is a n , when a1=a2=…=a n When the spiral cooling channel is a spiral line with equal pitch, the height of the spiral line is , in a1, a2, ..., a n When the pitch is not completely equal, the spiral cooling channel is a non-uniform helix. The width W of the bearing outer ring, the height h of the helix, and the length b of the flow channel of the cooling lubricating oil inlet satisfy the equation: .

[0024] The center line of the spiral cooling channel 106 is tangent to a line, and the tangent is a straight line or an arc with the center of curvature of the outer ring channel as the center. When the tangent is a straight line, the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel is the vertical distance between the straight line and the center of curvature of the outer ring channel; when the tangent is an arc, the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel is the radius of the arc.

[0025] The radius r of the bearing outer ring channel, the distance c between the tangent line of the spiral cooling channel centerline and the center of curvature of the outer ring channel, and the diameter d of the cooling channel cross section circle satisfy the inequality relationship: .

[0026] The value range of the width W of the bearing outer ring is [8d, 12d], the value range of the thickness T of the bearing outer ring is [2d, 8d], the value range of the outer diameter of the bearing outer ring is [45d, 53d], the value range of the groove bottom diameter of the bearing outer ring is [42d, 48d], the value range of the inner diameter of the bearing outer ring is [40d, 48d], the value range of the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel of the center line of the spiral cooling channel is [6d, 8d], and the value range of the radius r of the bearing outer ring channel is [5d, 6d].

[0027] A method for cooling and lubricating a bearing with a spiral cooling structure is characterized in that cooling and lubricating oil is introduced into an outer ring of the bearing with a spiral cooling structure to achieve cooling and lubrication, and specifically comprises the following steps: Step 1: The cooling lubricating oil is passed through the cooling lubricating oil inlet on one side of the bearing outer ring and into the spiral cooling flow channel through the cooling lubricating oil inlet flow channel. The cooling lubricating oil entering the spiral cooling flow channel finally flows out from the cooling lubricating oil outlet flow channel on the other side of the bearing outer ring, thereby completing the cooling of the bearing outer ring. Step 2: Pass the cooling lubricating oil into the bearing with a spiral cooling structure through the inner ring oil supply hole. The cooling lubricating oil flows through the bearing inner ring, retaining frame and balls to complete the cooling and lubrication of the bearing inner ring, retaining frame and balls.

[0028] The initial temperature of the cooling lubricating oil is 300K-350K, and the heat flux density is 100000W / m 2 ~200000W / m 2 , the oil supply flow rate is 0.5L / min~3L / min.

[0029] The initial temperature of the cooling lubricating oil is 323.15K, and the heat flux density is 150000W / m 2 , the oil supply flow rate is 2.5L / min.

[0030] In specific implementation, the width W of the bearing outer ring 103 is selected to be 40 mm, the outer diameter of the bearing outer ring 103 is 200 mm, the groove bottom diameter of the bearing outer ring 103 is 189 mm, the inner diameter of the bearing outer ring 103 is 178 mm, the thickness T of the bearing outer ring is 11 mm, and the groove radius r of the bearing outer ring 103 is 11.5 mm. A cooling lubricating oil inlet flow channel parallel to the axial direction, a spiral cooling flow channel and a cooling lubricating oil outlet flow channel parallel to the axial direction are arranged inside the bearing outer ring 103, and the flow channel cross-sectional circular diameter d is 4 mm. The length b of the cooling lubricating oil inlet flow channel and the cooling lubricating oil outlet flow channel is 5 mm. The center line of the spiral cooling flow channel is tangent to a straight line 14 mm away from the center of curvature of the outer ring channel. The number of spiral turns n of the spiral cooling flow channel is 3.5, and the pitch is equal and is 8.57 mm. The number of spiral turns n, the pitch a and the length b of the cooling lubricating oil inlet and outlet channels of the spiral cooling channel are set according to actual needs, so as to achieve efficient cooling of the bearing outer ring 103 .

[0031] As a specific solution of this embodiment, the flow channel of the cooling lubricating oil inlet 107 and the flow channel of the cooling lubricating oil outlet 108 are placed on different sides of the bearing outer ring 103, and the flow channel lengths of the cooling lubricating oil inlet 107 and the cooling lubricating oil outlet 108 are both b, and are distributed in a centrally symmetrical manner relative to the bearing outer ring 103.

[0032] As a specific solution of this embodiment, the spiral cooling channel 106 starts from the end of the channel of the cooling lubricating oil inlet and ends at the beginning of the channel of the cooling lubricating oil outlet, and the pitch a is constant; the width W of the bearing outer ring 103, the pitch a of the spiral cooling channel 103, and the length b of the channel of the cooling lubricating oil inlet 107 satisfy the equation .

[0033] In this embodiment, the bearing outer ring 103 with a spiral cooling structure is processed by metal 3D printing technology, with a printing accuracy of ≯0.05mm and an internal roughness of the hollow flow channel ≯Ra1.

[0034] In this embodiment, in order to verify the effect of the present invention on reducing the temperature, simulation calculations were performed using ANSYS software. During the calculation, for the multi-channel annular cooling structure described in the prior art and the spiral cooling structure proposed in the present invention, the maximum temperature of the fluid domain and the maximum temperature of the solid domain of the two structures under the given working conditions of this embodiment are shown in Table 1. The fluid domain is the cooling lubricating oil, and the solid domain is the outer ring of the bearing. It can be seen from Table 1 that under the same working conditions, compared with the multi-channel annular cooling structure, the maximum temperature of the fluid domain of the spiral cooling structure decreased by 15.5%, and the maximum temperature of the solid domain of the spiral cooling structure decreased by 2.2%. From the above analysis, it can be seen that the spiral cooling structure proposed in the present invention includes a cooling lubricating oil inlet flow channel parallel to the axial direction, a spiral cooling flow channel and a cooling lubricating oil outlet flow channel parallel to the axial direction. Compared with the multi-channel annular cooling structure, it can reduce the maximum temperature of the outer ring of the bearing and the cooling lubricating oil.

[0035] Table 1

[0036] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A ball bearing with a spiral cooling structure, characterized in that: It includes a bearing inner ring, a bearing outer ring, a retaining frame and a plurality of balls arranged circumferentially on the retaining frame coaxially arranged in the bearing. A spiral cooling channel is arranged inside the bearing outer ring, and the spiral cooling channel has an axis at the center of the bearing as the spiral axis. A cooling lubricating oil inlet and a cooling lubricating oil outlet connected to the spiral cooling channel are also arranged inside the bearing outer ring, and an inner ring oil supply hole for supplying oil to the balls is arranged through the bearing inner ring.

2. A ball bearing with a spiral cooling structure as claimed in claim 1, characterized in that: The flow channels of the cooling and lubricating oil inlet and the cooling and lubricating oil outlet are both arranged parallel to the bearing axis direction; the flow channel cross-sections of the cooling and lubricating oil inlet and the cooling and lubricating oil outlet are circular cross-sections; the cross-section of the spiral cooling flow channel is a circular cross-section, the spiral cooling flow channel is tangent to the flow channels of the cooling and lubricating oil inlet and the cooling and lubricating oil outlet, and the cross-section circle diameters of the spiral cooling flow channel, the cooling and lubricating oil inlet and the cooling and lubricating oil outlet are all d.

3. A ball bearing with a spiral cooling structure as claimed in claim 1 or 2, characterized in that: The flow channel of the cooling lubricating oil inlet and the flow channel of the cooling lubricating oil outlet are placed on different sides of the outer ring of the ball bearing. The flow channels of the cooling lubricating oil inlet and the cooling lubricating oil outlet are both b in length and are centrally symmetrically distributed relative to the outer ring of the bearing.

4. A ball bearing with a spiral cooling structure as claimed in claim 1 or 2, characterized in that: The spiral cooling channel starts from the end of the channel at the cooling lubricating oil inlet and ends at the beginning of the channel at the cooling lubricating oil outlet. The number of spiral turns is n. Starting from the starting point of the spiral cooling channel, the pitch of the first turn is a1, the pitch of the second turn is a2, and the pitch of the nth turn is a n , when a1=a2=…=a n When the spiral cooling channel is a spiral line with equal pitch, the height of the spiral line is , in a1, a2, ..., a n When the pitch is not completely equal, the spiral cooling channel is a non-uniform helix. The width W of the bearing outer ring, the height h of the helix, and the length b of the flow channel of the cooling lubricating oil inlet satisfy the equation: .

5. A ball bearing with a spiral cooling structure as claimed in claim 4, characterized in that: The center line of the spiral cooling channel is tangent to a line, and the tangent is a straight line or an arc with the center of curvature of the outer ring channel as the center. When the tangent is a straight line, the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel is the vertical distance between the straight line and the center of curvature of the outer ring channel; when the tangent is an arc, the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel is the radius of the arc.

6. A ball bearing with a spiral cooling structure as claimed in claim 5, characterized in that: The radius r of the outer ring channel, the distance c between the tangent line of the spiral cooling channel centerline and the center of curvature of the outer ring channel, and the diameter d of the cooling channel cross section circle satisfy the inequality relationship: .

7. A ball bearing with a spiral cooling structure as claimed in claim 1 or 2, characterized in that: The value range of the width W of the bearing outer ring is [8d, 12d], the value range of the thickness T of the bearing outer ring is [2d, 8d], the value range of the outer diameter of the bearing outer ring is [45d, 53d], the value range of the groove bottom diameter of the bearing outer ring is [42d, 48d], the value range of the inner diameter of the bearing outer ring is [40d, 48d], the value range of the distance c between the tangent of the center line of the spiral cooling channel and the center of curvature of the outer ring channel of the center line of the spiral cooling channel is [6d, 8d], and the value range of the radius r of the bearing outer ring channel is [5d, 6d].

8. A method for cooling and lubricating a bearing having a spiral cooling structure as claimed in claims 1 to 7, characterized in that: The cooling lubricating oil is introduced into the outer ring of the bearing with a spiral cooling structure to realize cooling lubrication, including the following steps: Step 1: The cooling lubricating oil is passed through the cooling lubricating oil inlet on one side of the bearing outer ring and into the spiral cooling flow channel through the cooling lubricating oil inlet flow channel. The cooling lubricating oil entering the spiral cooling flow channel finally flows out from the cooling lubricating oil outlet flow channel on the other side of the bearing outer ring, thereby completing the cooling of the bearing outer ring. Step 2: Pass the cooling lubricating oil into the bearing with a spiral cooling structure through the inner ring oil supply hole. The cooling lubricating oil flows through the bearing inner ring, retaining frame and balls to complete the cooling and lubrication of the bearing inner ring, retaining frame and balls.

9. A method for cooling and lubricating a bearing with a spiral cooling structure as claimed in claim 8, characterized in that: The initial temperature of the cooling lubricating oil is 300K-350K, and the heat flux density is 100000W / m 2 ~200000W / m 2 , the oil supply flow rate is 0.5L / min~3L / min.

10. A bearing cooling and lubrication method with a spiral cooling structure as claimed in claim 8, characterized in that: The initial temperature of the cooling lubricating oil is 323.15K, and the heat flux density is 150000W / m 2 , the oil supply flow rate is 2.5L / min.

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