An end face micro-texture and a kinematic pair of a mechanical bearing device

Abstract

The present invention provides an end face micro-texture structure for the end faces of mating kinematic pairs, which includes a plurality of hydrodynamic pressure units spaced apart along the relative movement direction of the kinematic pairs. Each hydrodynamic pressure unit includes a recessed drainage groove and Tesla one-way valve flow channel groove structures arranged on both sides of the drainage groove. The extending direction of the drainage groove is perpendicular to the relative movement direction of the end faces of the kinematic pairs. The flow channel contour shapes of the Tesla one-way valve flow channel groove structures on both sides of the drainage groove are symmetrical about the central axis of the drainage groove. This design can ensure that the fluid meets the conditions for generating the hydrodynamic pressure effect regardless of whether the kinematic pairs move relative to each other in the forward or reverse direction, ensuring that the kinematic pairs utilize the fluid to produce good support or sealing effects, and solving the problem that existing kinematic pairs can only provide unilateral support or sealing effects. The present invention also provides a kinematic pair of a mechanical bearing device.

Description

Technical Field

[0001] The present invention relates to the technical fields of fluid and microtexture, and in particular, to an end face microtexture structure, and also to a kinematic pair of a mechanical bearing device. Background Art

[0002] At present, devices such as gas lubricated thrust bearings, sliding bearings, mechanical seals, dry gas seals, etc. usually have a kinematic pair formed by a static part and a moving part. Its basic principle is to open micron-scale fluid lubrication grooves with special designed shapes on one surface of the kinematic pair. These grooves can shear the medium when the kinematic pair moves relatively, forming a hydrodynamic pressure effect, thereby generating a lifting force, so that a micron-scale gap is always maintained between the kinematic pairs, thus achieving functions such as reducing friction, taking away heat, providing bearing capacity, and providing controllable leakage. Such hydrodynamic pressure grooves are usually divided into single-rotation and double-rotation types. The single-rotation grooves include, for example, Archimedes spiral grooves, etc., and the double-rotation grooves include, for example, T-shaped grooves, Christmas tree grooves, etc. However, the unidirectional groove type was usually considered to be able to generate the maximum hydrodynamic pressure effect in the same industry in the past, while the hydrodynamic pressure effect generated by the bidirectional groove is relatively weak. However, in actual use, bearing and sealing devices often have the working requirement of bidirectional movement. Therefore, the current design of arranging the hydrodynamic pressure groove structure on the surface of the end face of the kinematic pair often fails to meet the actual working requirements of bearing and sealing components, etc., and the achieved bearing, lubrication and controllable leakage effects often have to be discounted.

[0003] In summary, the existing bearing and sealing devices with a hydrodynamic pressure groove surface design have the technical problem of poor performance during bidirectional movement. Summary of the Invention

[0004] The technical problem to be solved by the present invention is that the existing bearing and sealing devices with a hydrodynamic pressure groove surface design have the technical problem of poor performance during bidirectional movement. To solve the above problem, the present invention provides an end face microtexture structure for the end faces where kinematic pairs cooperate with each other, including a plurality of hydrodynamic pressure units spaced along the relative movement direction of the kinematic pairs. Each of the hydrodynamic pressure units includes a sunken drainage groove and Tesla one-way valve flow channel groove structures arranged on both sides of the drainage groove. The extending direction of the drainage groove is perpendicular to the relative movement direction of the end face of the kinematic pair, and one end of the drainage groove extends to the edge of the end face. The flow channel contour shapes of the Tesla one-way valve flow channel groove structures on both sides of the drainage groove are symmetrical about the central axis of the drainage groove.

[0005] The end-face micro-texture structure provided by the present invention is used for the end faces of kinematic pairs of devices such as thrust bearings, sliding bearings, mechanical seals, and dry gas seals. Its principle is that the relative movement of the kinematic pair drives the fluid movement to form a hydrodynamic pressure effect, thereby generating a lifting force, so that a micron-level gap is always maintained between the kinematic pairs, thus achieving functions such as reducing friction, removing heat, providing load-bearing capacity, and providing controllable leakage. Specifically, multiple axially arranged hydrodynamic pressure units are provided on the end face. The hydrodynamic pressure units are all axially symmetric structures, and a drainage groove is arranged at the central axis position. The end of the drainage groove extends to the edge of the end face for communicating with the fluid space on the side of the structure to introduce the fluid to the end face. On both sides of the drainage groove, Tesla one-way valve flow channel groove structures are symmetrically distributed. The Tesla one-way valve flow channel groove structures have the structural characteristics of Tesla one-way valves. When high-speed fluid flows from the drainage groove to the Tesla one-way valve flow channel groove structures on both sides, the turbulence generated inside the flow channel blocks the fluid flow, thus meeting the conditions for generating the hydrodynamic pressure effect. Further, since the flow channel structures of the Tesla one-way valve flow channel groove structures on both sides of the drainage groove are axially symmetric about the drainage groove, that is, when the fluid flows through the Tesla one-way valve flow channel groove structures perpendicular to the extension direction of the drainage groove on the end face of the kinematic pair, whether it passes forward or backward and corresponding to the forward or backward relative movement of the kinematic pair, it can ensure that the fluid meets the conditions for generating the hydrodynamic pressure effect, ensuring that the kinematic pair uses the fluid to produce a good support or sealing effect, and effectively solving the technical problem that the existing bearings and sealing devices with hydrodynamic pressure groove surface design have poor effects during bidirectional movement.

[0006] As a preferred solution, on both sides of the drainage groove, more than three groups of the above-mentioned Tesla one-way valve flow channel groove structures are evenly distributed at preset intervals along the extension direction of the drainage groove. The principle of this design is similar to the above design. By increasing the Tesla one-way valve flow channel groove structures arranged axially in sequence along the drainage groove, the hydrodynamic pressure effect is enhanced to improve the support or sealing effect on the kinematic pair.

[0007] As a preferred solution, the Tesla one-way valve flow channel groove structure includes a main flow channel communicating with the drainage groove. A plurality of branch flow channels communicating with the main flow channel are arranged at a preset interval on the side of the main flow channel. The branch flow channel includes an arc portion and a straight portion. The proximal ends of the arc portion and the straight portion are connected to each other, and the distal ends of the arc portion and the straight portion are respectively connected to the main flow channel. A preset angle is formed between the straight portion and the main flow channel. This design optimizes the specific structure of the Tesla one-way valve flow channel groove structure. The process of the hydrodynamic pressure effect passing through the Tesla one-way valve flow channel is that high-speed fluid enters the main flow channel from the drainage groove. When the fluid passes along the direction from the arc flow channel to the straight flow channel of the branch flow channel, the turbulence generated when the fluid flows back from the branch flow channel to the main flow channel blocks the fluid flow, thus meeting the conditions for generating the hydrodynamic pressure effect.

[0008] As a preferred solution, a hydrodynamic pressure groove structure is provided between adjacent hydrodynamic pressure units. One end of the hydrodynamic pressure groove structure in the long axis direction extends to the edge of the end face. Both sides of the hydrodynamic pressure groove structure are respectively communicated with the Tesla one-way valve flow channel groove structures of adjacent hydrodynamic pressure units, and the contour shapes of the two Tesla one-way valve flow channel groove structures are symmetrical about the central axis of the hydrodynamic pressure groove structure.

[0009] This design further improves the adaptability between the end face micro-texture structure and the kinematic pair structure. A hydrodynamic pressure groove structure is provided between adjacent hydrodynamic pressure units. The groove depth of the hydrodynamic pressure groove is preferably larger than that of the groove structure of the hydrodynamic pressure unit. The additional groove structure increases the flux of the fluid, so as to strengthen the basic lubrication function required for the end face while meeting the support and sealing function requirements of the end face, enabling the fluid medium to better communicate with the lubrication passages at other positions of the kinematic pair.

[0010] As a preferred solution, the groove depth of the hydrodynamic pressure groove structure on the end face is 1.5 to 2.5 times that of the groove depth of the hydrodynamic pressure unit. This design specifically optimizes the ratio of the groove depth of the hydrodynamic pressure groove structure to the groove depth of the hydrodynamic pressure unit. The numerical ratio range of the groove depths of the two is preferably 1.5 to 2.5 times. Such a groove depth design can further optimize the above-mentioned situation on the premise of ensuring the support and sealing effects of the kinematic pair end face, increase the flow rate of the fluid medium at the kinematic pair end face, and meet the working requirements of the overall kinematic pair.

[0011] As a preferred solution, the ratio of the length of the hydrodynamic pressure groove structure in the relative movement direction of the kinematic pair to the length of the hydrodynamic pressure unit ranges from 1:1 to 1.5:1. This design is for the end face design with the hydrodynamic pressure unit and the hydrodynamic pressure groove distributed at intervals. Adopting this length coverage ratio can balance and optimize the support and lubrication effects of the kinematic pair.

[0012] As a preferred solution, the hydrodynamic pressure groove structure is in a T shape. The end of the groove body structure where the central axis of the hydrodynamic pressure groove structure is located extends to the edge of the end face, and the end parts of the groove body structures on both sides of the hydrodynamic pressure groove structure are respectively communicated with the Tesla one-way valve flow channel groove structures of adjacent hydrodynamic pressure units.

[0013] This design provides a preferred hydrodynamic pressure groove structure. The overall structure is in a T shape. The end of the middle groove body reaches the edge of the end face. The two side groove bodies are communicated with the other end of the middle groove body, and are communicated with the adjacent Tesla one-way valve flow channel groove structure at the other end. The fluid passing performance of this structure is good and is suitable for the above-mentioned groove body design requirements.

[0014] As a preferred solution, the lengths of each section and the total length of the drainage groove of the hydrodynamic pressure unit and the Tesla one-way valve flow channel groove structure are all greater than 1 mm, and the groove depth values of the drainage groove and the Tesla one-way valve flow channel groove structure on the end face range from 0.1 μm to 100 μm.

[0015] This design optimizes the dimensions of the drainage groove of the hydrodynamic pressure unit and the Tesla one-way valve flow channel groove structure. The length and width of the drainage groove and the Tesla one-way valve flow channel groove structure in the plane of the end face of the kinematic pair are both millimeter-level, and the length of each groove section is greater than 1 mm. The dimension of the drainage groove and the Tesla one-way valve flow channel groove structure in the thickness direction of the end face, that is, the groove depth, is micron-level. The preferred groove depth range is from 0.1 μm to 100 μm. The optimization of the size of this groove shape in the two-dimensional plane of the end face can first ensure that the groove body size is large enough to ensure that the turbulence formed by the fluid can provide sufficient supporting force. Secondly, the groove depth in the thickness direction is micron-level, avoiding the increase of the roughness of the end face and the increase of the frictional force of the end face due to the excessive groove depth on the end face, which affects the normal working performance of the kinematic pair.

[0016] As a preferred solution, the groove width value range of the drainage groove is 0.5 mm - 50 mm, including the end point values, and the groove width value ranges of the main flow channel and the sub-flow channel are 0.1 mm - 2 mm, including the end point values. This design is a further optimization based on the above-mentioned groove structure dimensions, providing the preferred size ranges of the groove widths of the drainage groove, the main flow channel and the sub-flow channel. Within this groove width value range, it can ensure that the flow rate of the fluid medium meets the conditions for forming the hydrodynamic pressure effect, and can reduce the processing difficulty of the groove structure on the end face through the limitation of the groove width size, reducing the actual cost of the equipment.

[0017] The present invention also provides a kinematic pair of a mechanical bearing device, including kinematic pair mating members with end faces abutted against each other. The kinematic pair mating members are in a circular ring shape or a flat plate shape, and the end faces of the kinematic pair mating members are provided with the end face micro-texture structure as described in any one of the above. When the kinematic pair mating members are both in a circular ring shape, the hydrodynamic pressure units are distributed in a circular array; when the kinematic pair mating members are in a flat plate shape, the hydrodynamic pressure units are distributed in a linear array. Due to the above various beneficial effects of the end face micro-texture structure, the kinematic pair of the mechanical bearing device with this end face micro-texture structure should also have corresponding beneficial effects. Description of the Drawings

[0018] Figure 1 It is a partial structural schematic diagram of a single hydrodynamic pressure unit in an end face micro-texture structure provided by the present invention;

[0019] Figure 2 is Figure 1 a partial structural schematic diagram of the end face micro-texture structure;

[0020] Figure 3 Schematic diagram of the end face structure of a kinematic pair of a mechanical bearing device provided by the present invention;

[0021] Figure 4 Schematic diagram of the principle of the Tesla check valve.

[0022] Among them, Figures 1-3 In:

[0023] 1. Drainage groove; 2. Groove structure of the flow channel of the Tesla check valve; 2-1. Main flow channel; 2-2. Sub-flow channel; 2-2-1. Arc part; 2-2-2. Straight part; 3. Fluid dynamic pressure groove structure; 4. Kinematic pair mating member. Specific embodiments

[0024] In order to make the technical means, creative features, achieved purposes and effects of the present invention easy to understand, the present invention will be further described below in conjunction with specific embodiments. Before making a detailed description of the working principle of the present invention, it is also necessary to further explain the description of the present invention: In the description of the present invention, it should be noted that the terms "upper", "lower", "inner", "outer", "front end", "rear end", "both ends", "one end", "the other end", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance.

[0025] In the description of the present invention, it should be noted that unless otherwise clearly specified and limited, the terms "installed", "provided with", "connected", etc. should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, a direct connection, an indirect connection through an intermediate medium, or a welded connection between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0026] Refer to Figures 1-4 The following embodiments are described as follows. Figure 1 Schematic diagram of the partial structure of a single fluid dynamic pressure unit in the end face micro-texture structure provided by the present invention; Figure 2 For Figure 1 Partial structure schematic diagram of the end face micro-texture structure in Figure 3 Schematic diagram of the end face structure of a kinematic pair of a mechanical bearing device provided by the present invention; Figure 4 Schematic diagram of the principle of the Tesla check valve.

[0027] An embodiment of the present invention provides an end face micro-texture structure, which includes a plurality of hydrodynamic pressure units arranged regularly in an array. Each hydrodynamic pressure unit includes a concave drainage groove 1 and Tesla one-way valve channel groove structures 2 symmetrically arranged on both sides of the drainage groove 1. The extending direction of the drainage groove 1 is perpendicular to the relative movement direction of the end face. One end of the drainage groove 1 extends to the edge of the end face. The Tesla one-way valve channel groove structure 2 includes a main channel 2-1 communicating with the drainage groove 1. A plurality of branch channels 2-2 communicating with the main channel 2-1 are arranged at intervals of a preset distance on the side of the main channel 2-1. The branch channel 2-2 includes an arc portion 2-2-1 and a straight portion 2-2-2. The proximal ends of the arc portion 2-2-1 and the straight portion 2-2-2 communicate with each other. The distal ends of the arc portion 2-2-1 and the straight portion 2-2-2 are respectively communicated with the main channel 2-1. The included angle between the straight portion 2-2-2 and the main channel 2-1 is a preset angle less than 45°. The channel contour shapes of the main channels 2-1 and the branch channels 2-2 of the Tesla one-way valve channel groove structures 2 on both sides of the drainage groove 1 are symmetric about the central axis of the drainage groove 1.

[0028] The present invention is implemented at the micro-nano scale by using the shape characteristics of the Tesla valve and utilizes the one-way passage characteristic of the Tesla one-way valve. As Figure 4 shown, when the high-speed fluid flows from right to left, due to the special structure, no turbulence will be generated at the Tesla valve section to block the fluid. However, when the high-speed fluid flows from left to right, the fluid will generate turbulence at the Tesla valve section to block the fluid, thereby realizing the one-way passage ability of the entire flow channel.

[0029] This end face micro-texture structure provided by the present invention is used to be arranged on the moving pair end faces of equipment such as thrust bearings, sliding bearings, mechanical seals, and dry gas seals. Its principle is that the relative movement of the moving pair drives the fluid movement to form a hydrodynamic pressure effect, thereby generating a lifting force, so that a micron-level gap is always maintained between the moving pairs, thereby achieving functions such as reducing friction, taking away heat, providing bearing capacity, and providing controllable leakage. Specifically, a plurality of fluid dynamic pressure units arranged in an array are provided on the end face. The fluid dynamic pressure units are all axially symmetric structures. A drainage groove 1 is arranged at the central axis position. The end of the drainage groove 1 extends to the edge of the end face and is used to communicate with the fluid space on the side of the structure to introduce the fluid into the end face. The Tesla one-way valve channel groove structures 2 are symmetrically distributed on both sides of the drainage groove 1. The forming methods of the configurations of the drainage groove 1 and the Tesla one-way valve channel groove structures 2 on the end face include but are not limited to lithography, laser, or chemical etching and other methods.

[0030] The Tesla one-way valve flow channel groove structure 2 has the structural characteristics of a Tesla valve. When high-speed fluid passes through in the direction from the arc flow channel of the shunt channel 2-2 to the straight flow channel, the turbulence generated when the fluid flows back from the shunt channel 2-2 to the main flow channel 2-1 blocks the flow of the fluid, thus meeting the conditions for generating the hydrodynamic pressure effect. Further, due to the fact that the flow channel structure shapes of the Tesla one-way valve flow channel groove structures 2 on both sides of the drainage groove 1 are axisymmetric with respect to the drainage groove 1, that is, when the fluid flows through the Tesla one-way valve flow channel groove structure 2 perpendicular to the movement direction of the drainage groove 1 on the moving pair end face, whether it passes through in the forward or reverse direction, corresponding to the forward or reverse relative movement of the moving pair, the fluid can form a fluid circulation area in the area of the Tesla one-way valve flow channel groove structure 2 on one side of the drainage groove 1 and a fluid blockage area on the other side of the drainage groove 1. It can be seen that regardless of the relative movement direction of the moving pair end face, the fluid can meet the conditions for generating the hydrodynamic pressure effect on the end face, ensuring that the moving pair can utilize the fluid to generate good support or sealing effects, effectively solving the technical problem that the existing bearings and sealing devices using hydrodynamic groove surface design have poor effects during bidirectional movement.

[0031] In the technical solution provided in this embodiment, shunt channels 2-2 are provided on both sides of each main flow channel 2-1, and the inclination angles of the straight portions 2-2-2 and the arc portions 2-2-1 of the respective shunt channels 2-2 located on both sides of the main flow channel are symmetric with respect to the main flow channel 2-1. This design optimizes the structure of each Tesla one-way valve flow channel groove structure 2. Multiple shunt channels 2-2 are provided on both sides of the main flow channel 2-1, and structurally, it is ensured that the inclination angles of the straight portions 2-2-2 and the arc portions 2-2-1 of the respective shunt channels 2-2 located on both sides of the main flow channel 2-1 are symmetric with respect to the main flow channel 2-1, so as to ensure that the fluid movement directions of the fluid turbulences generated by the shunt channels 2-2 on both sides are the same. Through such a design, the positions where each side of the Tesla one-way valve flow channel groove structure 2 can generate turbulence are increased, which is equivalent to enhancing the hydrodynamic pressure effect and improving the support or sealing effect on the moving pair.

[0032] In the technical solution provided in this embodiment, for the same Tesla one-way valve flow channel groove structure 2, the lengths of the flow channels 2-2 on both sides of the main flow channel 2-1 in each shunt channel are equal to the distance between adjacent shunt channels 2-2, and the shunt point of any shunt channel 2-2 and the main flow channel 2-1 coincides with the confluence point of the adjacent shunt channel 2-2 on the other side and the main flow channel 2-1. This design further optimizes the specific structure of each Tesla one-way valve flow channel groove structure 2. On the basis of the structure with connected shunt channels 2-2 provided on both sides of the main flow channel 2-1, the flow channel shapes and lengths of the shunt channels 2-2 are equal, and the shunt or confluence positions of the shunt channels 2-2 adjacent to each other on both sides of the main flow channel 2-1 and the main flow channel 2-1 coincide exactly. Through hydrodynamic analysis, adopting such a flow channel design can enhance the intensity of the turbulence generated at the confluence position of the shunt channel 2-2 and the main flow channel 2-1. Enhancing the intensity of the turbulence is equivalent to enhancing the intensity of the hydrodynamic pressure effect, and it can also improve the support or sealing effect of the fluid on the kinematic pair.

[0033] In the technical solution provided in this embodiment, on both sides of the drainage groove 1, more than three groups of Tesla one-way valve flow channel groove structures 2 are evenly distributed at preset intervals along the extension direction of the drainage groove 1. This design is similar to the above design principle. By increasing the Tesla one-way valve flow channel groove structures 2 arranged in sequence along the axis of the drainage groove 1, the hydrodynamic pressure effect is enhanced to improve the support or sealing effect on the kinematic pair.

[0034] In the technical solution provided in this embodiment, a hydrodynamic pressure groove structure 3 is provided between adjacent hydrodynamic pressure units. One end of the long axis direction of the hydrodynamic pressure groove structure 3 extends to the edge of the end face. The two sides of the hydrodynamic pressure groove structure 3 are respectively connected to the Tesla one-way valve flow channel groove structures 2 of the adjacent hydrodynamic pressure units, and the contour shapes of the shunt channels 2-2 of the Tesla one-way valve flow channel groove structures 2 on both sides are symmetrical about the center axis of the hydrodynamic pressure groove structure 3.

[0035] This design further improves the adaptability between the end face micro-texture structure and the kinematic pair structure. A hydrodynamic pressure groove structure 3 is provided between adjacent hydrodynamic pressure units. The groove of the hydrodynamic pressure groove relative to the groove structure of the hydrodynamic pressure unit preferably has a greater groove depth. By means of such an additional groove structure, the flux of the fluid is increased, so that in addition to meeting the required support and sealing function requirements of the end face, the basic lubrication function required by the end face is strengthened, and the fluid medium can better communicate with the lubrication passages at other positions of the kinematic pair.

[0036] In the technical solution provided in this embodiment, the groove depth of the hydrodynamic groove structure 3 at the end face is 1.5 to 2.5 times the groove depth of the hydrodynamic unit groove. This design specifically optimizes the ratio of the groove depth of the hydrodynamic groove structure 3 to the groove depth of the hydrodynamic unit. The numerical ratio range of the groove depths of the two is preferably 1.5 to 2.5 times, and most preferably 2 times. Such a groove depth design can further optimize the above-mentioned conditions of ensuring the end face support and sealing effect of the kinematic pair, increasing the flow rate of the fluid medium at the end face of the kinematic pair to meet the working requirements of the overall kinematic pair. At the same time, the ratio range of the length of the hydrodynamic groove structure in the relative movement direction of the kinematic pair to the length of the hydrodynamic unit is 1:1 - 1.5:1, where the length of the hydrodynamic unit refers to the length of the hydrodynamic unit in the relative movement direction of the kinematic pair. This design is for the end face design with the hydrodynamic unit and the hydrodynamic groove distributed at intervals. Using this length coverage ratio can take into account optimizing the support and lubrication effects of the kinematic pair.

[0037] In the technical solution provided in this embodiment, the hydrodynamic groove structure 3 is in a T shape. The end of the groove body structure where the central axis of the hydrodynamic groove structure 3 is located extends to the edge of the end face. The end parts of the groove body structures on both sides of the hydrodynamic groove structure 3 are respectively connected to the Tesla one-way valve flow channel groove structure 2 of the adjacent hydrodynamic unit.

[0038] This design provides a preferred hydrodynamic groove structure 3. The overall structure is in a T shape. The end of the middle groove body reaches the edge of the end face. The groove bodies on both sides are connected to the other end of the middle groove body and are connected to the adjacent Tesla one-way valve flow channel groove structure 2 at the other end. The fluid passing performance of this structure is good and is suitable for the above-mentioned groove body design requirements.

[0039] In this embodiment, the hydrodynamic groove structure 3 is preferably a T-shaped groove, or it can also be a two-way hydrodynamic groove of other known technologies or other inventions. When this type of groove moves linearly to one side or rotates in a certain direction in the kinematic pair where the end face is located, a hydrodynamic positive pressure will be formed in the area where the Tesla one-way valve flow channel groove structure 2 is located on one side of the T-shaped groove, and a hydrodynamic negative pressure will be formed in the area where the Tesla one-way valve flow channel groove structure 2 is located on the other side of the T-shaped groove. After the positive and negative pressures cancel each other out, the total hydrodynamic pressure value is extremely low.

[0040] Due to the characteristics of the micro-texture unit being symmetric left and right and one opening and one closing, the fluid (liquid or gas) replenished into the drainage groove 1 area can smoothly pass through the Tesla one-way valve flow channel groove structure 2 on one side of the drainage groove 1 to eliminate the negative pressure area on one side of the T-shaped groove. However, the high-pressure fluid medium on the other side of the T-shaped groove cannot enter the area on the other side of the T-shaped groove due to the blocking effect of the Tesla flow channel characteristics, thus realizing the fluid blocking function between the positive pressure area and the Tesla flow channel micro-texture area and the function of replenishing the medium to the negative pressure area to reduce the negative pressure. Thus, the negative pressure area of the two-way groove friction pair with the Tesla flow channel micro-texture characteristics is completely eliminated, and the positive pressure area is retained.

[0041] In the technical solution provided by this embodiment, the lengths of each section and the total length of the drainage groove 1 of the hydrodynamic pressure unit and the Tesla one-way valve flow channel groove structure 2 are all greater than 1 mm, and the groove depth value range of the drainage groove 1 and the Tesla one-way valve flow channel groove structure 2 on the end face is 0.1 μm - 100 μm.

[0042] This design optimizes the dimensions of the drainage groove 1 of the hydrodynamic pressure unit and the Tesla one-way valve flow channel groove structure 2. The length and width of the drainage groove 1 and the Tesla one-way valve flow channel groove structure 2 in the plane of the end face of the kinematic pair are both in millimeters. The lengths of each groove section, including the main flow channel 2-1, the branch flow channels 2-1, the straight part 2-2-2 and the arc part 2-2-1 of the branch flow channels 2-1, are all greater than 1 mm. The dimension of the drainage groove 1 and the Tesla one-way valve flow channel groove structure 2 in the thickness direction of the end face, that is, the groove depth, is in microns. The preferred groove depth value range is 0.1 μm - 100 μm. The optimization of the dimensions of this groove shape in the two-dimensional plane of the end face can first ensure that there is a sufficiently large groove body size to ensure that the turbulent flow formed by the fluid can provide sufficient supporting force. Secondly, the groove depth in the thickness direction is in microns, avoiding an excessive groove depth on the end face that increases the roughness of the end face and increases the frictional force on the end face, thus affecting the normal working performance of the kinematic pair.

[0043] In the technical solution provided by this embodiment, the groove width value range of the drainage groove 1 is 0.5 mm - 50 mm, including the end values, and the groove width value ranges of the main flow channel 2-1 and the branch flow channels 2-2 are 0.1 mm - 2 mm, including the end values. This design is a further optimization based on the above groove structure dimensions, providing the preferred dimension ranges of the groove widths of the drainage groove 1, the main flow channel 2-1 and the branch flow channels 2-2. Within this groove width value range, it can ensure that the flow rate of the fluid medium meets the conditions for forming the hydrodynamic pressure effect, and can reduce the processing difficulty of the groove structure on the end face and the actual cost of the equipment by limiting the groove width dimensions.

[0044] This embodiment also provides a kinematic pair of a mechanical bearing device, which includes kinematic pair mating members 4 with end faces abutting against each other. The kinematic pair mating members include common ring-shaped and planar shapes. The end faces of the kinematic pair mating members 4 are provided with the end face micro-texture structures described in any of the above embodiments. It is only necessary to provide the end face micro-texture structure on one of the two mutually cooperating end faces. When the kinematic pair mating member is ring-shaped, that is, when it is a rotary bearing member, the hydrodynamic pressure units are distributed in a ring-shaped array, and the distribution method can be a single ring or multiple radially spaced rings. In the case of a multi-ring array, the drainage grooves 1 of the hydrodynamic pressure units located at the same circumferential position of adjacent rings are interconnected with each other. When the kinematic pair mating member 4 is in a flat plate shape or a similar guide rail-shaped structure, that is, when the two members support and lubricate each other by translational sliding, the hydrodynamic pressure units are distributed in a linear array, and it can also be adapted to the actual surface conditions of the member and be arrayed in a shape where multiple straight lines are parallel to each other. Since the above-mentioned end face micro-texture structure has the above various beneficial effects, the kinematic pair of the mechanical bearing device with this end face micro-texture structure should also have corresponding beneficial effects.

[0045] Although the present invention is disclosed as above, the protection scope of the present invention is not limited thereto. Those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present disclosure, and these changes and modifications will all fall within the protection scope of the present invention.

Claims

1. An end face micro-texture structure, characterized in that The end face for the mating of kinematic pairs includes a plurality of hydrodynamic pressure units spaced apart along the relative movement direction of the kinematic pairs. Each of the hydrodynamic pressure units includes a recessed drainage groove (1) and Tesla one-way valve channel groove structures (2) arranged on both sides of the drainage groove (1). The extending direction of the drainage groove (1) is perpendicular to the relative movement direction of the end face of the kinematic pair. One end of the drainage groove (1) extends to the edge of the end face. The channel contour shapes of the Tesla one-way valve channel groove structures (2) on both sides of the drainage groove (1) are symmetric about the central axis of the drainage groove (1). On both sides of the drainage groove (1), more than three groups of the Tesla one-way valve channel groove structures (2) are evenly distributed at preset intervals along the extending direction of the drainage groove (1).

2. The end face micro-texture according to claim 1, characterized in that, The Tesla one-way valve channel groove structure (2) includes a main channel (2-1) communicating with the drainage groove (1). A plurality of sub-channels (2-2) communicating with the main channel (2-1) are arranged at preset intervals on the side of the main channel (2-1). The sub-channel (2-2) includes an arc portion (2-2-1) and a straight portion (2-2-2). The proximal ends of the arc portion (2-2-1) and the straight portion (2-2-2) are connected to each other. The distal ends of the arc portion (2-2-1) and the straight portion (2-2-2) are respectively connected to the main channel (2-1). A preset angle is formed between the straight portion (2-2-2) and the main channel (2-1).

3. The end face micro-texture according to any one of claims 1 or 2, characterized in that, A hydrodynamic pressure groove structure (3) is arranged between adjacent hydrodynamic pressure units. One end of the hydrodynamic pressure groove structure (3) in the long axis direction extends to the edge of the end face. The two sides of the hydrodynamic pressure groove structure (3) are respectively connected to the Tesla one-way valve channel groove structures (2) of adjacent hydrodynamic pressure units. The contour shapes of the Tesla one-way valve channel groove structures (2) on both sides are symmetric about the central axis of the hydrodynamic pressure groove structure (3).

4. The end face micro-texture according to claim 3, characterized in that, The groove depth of the hydrodynamic pressure groove structure (3) on the end face is 1.5 to 2.5 times the groove depth of the hydrodynamic pressure unit.

5. The end face micro-texture according to claim 4, characterized in that, The ratio of the length of the hydrodynamic pressure groove structure (3) in the relative movement direction of the kinematic pair to the length of the hydrodynamic pressure unit ranges from 1:1 to 1.5:

1.

6. The end face micro-texture according to claim 4, characterized in that The hydrodynamic pressure groove structure (3) is in a T shape. The end of the groove structure where the central axis of the hydrodynamic pressure groove structure (3) is located extends to the edge of the end face. The end parts of the groove structures on both sides of the hydrodynamic pressure groove structure (3) are respectively connected to the Tesla one-way valve channel groove structures (2) of adjacent hydrodynamic pressure units.

7. The end face micro-texture according to claim 2, characterized in that, The lengths of each section and the total length of the drainage groove (1) and the Tesla one-way valve channel groove structure (2) of the hydrodynamic pressure unit are all greater than 1 mm. The numerical range of the groove depth of the drainage groove (1) and the Tesla one-way valve channel groove structure (2) on the end face is 0.1 μm to 100 μm.

8. The end face micro-texture structure according to claim 7, characterized in that, The numerical range of the groove width of the drainage groove (1) is 0.5 mm to 50 mm, including the end values. The numerical ranges of the groove widths of the main channel (2-1) and the sub-channel (2-2) are 0.1 mm to 2 mm, including the end values.

9. A kinematic pair of a mechanical bearing device, comprising kinematic pair mating members with end faces abutting against each other, the kinematic pair mating members being in a circular ring shape or a flat plate shape, characterized in that, The end face of the kinematic pair mating member is provided with the end face micro-texture structure as described in any one of claims 1-8. When the kinematic pair mating members are all annular, the hydrodynamic pressure units are distributed in an annular array; when the kinematic pair mating members are plate-shaped, the hydrodynamic pressure units are distributed in a linear array.

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