Fluid dynamic pressure groove, shaft core, bearing and shaft core bearing assembly with fast pressure buildup

Abstract

The utility model discloses a kind of fluid dynamic pressure grooves of quick pressure building, shaft core, bearing and shaft core bearing assembly, wherein, quick pressure building fluid dynamic pressure groove is arranged in the outer circumferential surface of shaft core or the inner cavity inner circumferential surface of bearing, it includes several groups of circumferential spacing V-shaped dynamic pressure groove around arrangement, each group V-shaped dynamic pressure groove includes two oblique grooves that meet into V shape, the intersection point of two oblique grooves of each group V-shaped dynamic pressure groove is regarded as pressure building center point;Oblique groove has at least two branch grooves and one acceleration groove, the flow starting point of the two branch grooves is separated from each other respectively, and extend towards pressure building center point direction, so that the flow endpoint of the two branch grooves is merged and connected with the flow starting point of acceleration groove, acceleration groove extends towards pressure building center point direction.Such, using the principle of im Tesla microchannel, realize the oblique groove of two sides gradually accelerates, and then realize the quick pressure building of each group V-shaped dynamic pressure groove, improve pressure building pressure.

Description

Technical Field

[0001] This utility model relates to the field of dynamic pressure shaft cores and shaft core bearing assemblies, and in particular to a rapid pressure-building fluid dynamic pressure groove, shaft core, bearing, and shaft core bearing assembly. Background Technology

[0002] Hydrodynamic bearings are widely used in various rotating machinery (such as turbines, compressors, motors, gearboxes, etc.). They are formed by filling the hydrodynamic grooves with dynamic lubricating fluid, which generates the hydrodynamic pressure of the lubricating fluid in the bearing clearance, thereby supporting the hydrodynamic shaft in a non-contact manner. They are suitable for high-speed rotation and have advantages such as high rotational accuracy, low noise and long service life.

[0003] Existing hydrodynamic bearings have an axially penetrating inner cavity for mounting a shaft core. Several sets of V-shaped hydrodynamic grooves are arranged circumferentially on the inner circumferential surface of the cavity. The intersection of the two grooves in each set of V-shaped hydrodynamic grooves serves as a pressure-building groove. As shown in CN221221149U, the two grooves in each set of V-shaped hydrodynamic grooves are regular oblique grooves. Theoretically, the oil velocity remains constant as it flows from the flow starting point of the groove towards the V-shaped apex. However, in reality, not all oil flows uniformly towards the V-shaped apex. Even the oil participating in the pressure-building flow encounters resistance during its flow. For regular oblique grooves, some oil will inevitably flow against the pressure-building direction. These factors limit the further development of rapid pressure-building technology.

[0004] However, for high-speed operation, higher requirements are placed on rapid pressure build-up, stable pressure build-up, and pressure maintenance, which are directly related to the smoothness and reliability of operation.

[0005] Therefore, it is necessary to research a new technical solution to address the above problems. Utility Model Content

[0006] In view of this, the present invention addresses the deficiencies of the existing technology and its main purpose is to provide a fluid dynamic pressure groove, shaft core, bearing and shaft core bearing assembly for rapid pressure building. It utilizes the Tesla-inspired microchannel principle to achieve gradual acceleration of the inclined grooves on both sides, thereby realizing rapid pressure building of each set of V-shaped dynamic pressure grooves and improving the pressure building pressure.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A rapid pressure-building fluid dynamic pressure trench includes several sets of V-shaped dynamic pressure trenches arranged around the perimeter. Each set of V-shaped dynamic pressure trenches includes two inclined trenches that intersect to form a V shape. The intersection point of the two inclined trenches in each set of V-shaped dynamic pressure trenches serves as the pressure-building center point.

[0009] The inclined groove has at least two branch grooves and an acceleration groove. The flow starting points of the two branch grooves are separate from each other and extend toward the pressure building center point, so that the flow ending points of the two branch grooves converge and connect to the flow starting point of the acceleration groove, which extends toward the pressure building center point.

[0010] As a preferred embodiment, the pressure-building center point extends towards the flared end of the V-shaped dynamic pressure groove with a widened groove.

[0011] As a preferred embodiment, the widened groove maintains a gap between its two sides and the two inclined grooves respectively;

[0012] Alternatively, the widened groove may be connected to two inclined grooves on both sides.

[0013] As a preferred embodiment, the acceleration trench has an acceleration section that gradually narrows along the flow direction; the trench area at the beginning of the acceleration section is less than or equal to the sum of the trench areas at the flow endpoints of the two branch trenches, and the trench area at the end of the acceleration section is less than the trench area at the beginning of the acceleration section.

[0014] As a preferred embodiment, auxiliary grooves are respectively connected to both sides of the pressure-building center point. The flow starting point of the auxiliary grooves is located outside the two inclined grooves, and the flow ending point of the auxiliary grooves merges and connects with the pressure-building center point.

[0015] As a preferred embodiment, a secondary pressure-building groove extends from the flared end of the V-shaped dynamic pressure groove away from the pressure-building center point. The flow endpoint of the auxiliary groove merges with the pressure-building center point and extends through the secondary pressure-building groove, so that the pressure-building center point is set as the pre-pressure-building center point, and the secondary pressure-building groove becomes the effective pressure-building center point.

[0016] As a preferred embodiment, the flow starting points of the branch trenches are arranged along the overall flow direction spacing of the inclined trenches.

[0017] A hydrodynamic shaft core includes a shaft core body, wherein a hydrodynamic groove region is recessed on the outer peripheral surface of the shaft core body, and the hydrodynamic groove region has a hydrodynamic groove for rapid pressure build-up as described in any of the preceding claims.

[0018] A hydrodynamic bearing includes a bearing body, wherein an axially penetrating inner cavity is formed within the bearing body, and a hydrodynamic groove region is provided on the inner circumferential surface of the inner cavity, wherein the hydrodynamic groove region has a hydrodynamic groove for rapid pressure build-up as described in any of the preceding claims.

[0019] A shaft bearing assembly includes a hydrodynamic bearing and a hydrodynamic shaft, wherein the hydrodynamic bearing has an axially penetrating inner cavity, and the hydrodynamic shaft is located in the inner cavity;

[0020] The outer circumferential surface of the fluid dynamic pressure shaft core is recessed with a dynamic pressure groove area. The dynamic pressure groove area has a fluid dynamic pressure groove for rapid pressure building as described in any of the preceding items. The fluid dynamic pressure bearing is fixed, while the fluid dynamic pressure shaft core rotates. The rotation direction of the fluid dynamic pressure shaft core is opposite to the flow pressure building direction of the V-shaped dynamic pressure groove.

[0021] Alternatively: the inner circumferential surface of the inner cavity is provided with a dynamic pressure groove area, the dynamic pressure groove area having a fluid dynamic pressure groove for rapid pressure building as described in any of the preceding items, the fluid dynamic pressure bearing is fixed, and the fluid dynamic pressure shaft core rotates; the rotation direction of the fluid dynamic pressure shaft core is the same as the flow pressure building direction of the V-shaped dynamic pressure groove.

[0022] Compared with existing technologies, this invention has significant advantages and beneficial effects. Specifically, as can be seen from the above technical solution, it mainly involves cleverly designing a traditional inclined groove into a multi-branched microchannel. This microchannel has at least two branch grooves and an acceleration groove. The flow initiation points of the two branch grooves are separate and extend towards the pressure-building center point. The flow endpoints of the two branch grooves converge and connect to the flow initiation point of the acceleration groove, which also extends towards the pressure-building center point. Thus, utilizing the principle of Tesla-inspired microchannels, the inclined grooves on both sides gradually accelerate, thereby achieving rapid pressure building in each set of V-shaped dynamic pressure grooves and increasing the pressure build-up pressure.

[0023] To more clearly illustrate the structural features and effects of this utility model, the following detailed description of this utility model is provided in conjunction with the accompanying drawings and specific embodiments. Attached Figure Description

[0024] Figure 1 This is a perspective view of the shaft core according to Embodiment 1 of this utility model;

[0025] Figure 2 This is a structural diagram of the dynamic pressure groove area of ​​the shaft core according to Embodiment 1 of this utility model;

[0026] Figure 3 This is a cross-sectional view of the shaft bearing assembly according to Embodiment 1 of this utility model;

[0027] Figure 4 This is a schematic diagram illustrating the principle of fluid velocity increasing along the confluence direction in a dynamic pressure trench according to Embodiment 1 of this utility model.

[0028] Figure 5 This is a schematic diagram illustrating the principle that the fluid velocity in the dynamic pressure trench slows down along the diversion direction in Embodiment 1 of this utility model.

[0029] Figure 6This is a structural diagram of a set of V-shaped dynamic pressure grooves in the dynamic pressure groove area of ​​the shaft core according to Embodiment 2 of this utility model;

[0030] Figure 7 This is a structural diagram of a set of V-shaped dynamic pressure grooves in the dynamic pressure groove area of ​​the shaft core according to Embodiment 3 of this utility model;

[0031] Figure 8 This is an exploded view of the bearing and shaft core according to Embodiment 4 of this utility model;

[0032] Figure 9 This is a cross-sectional view of the shaft bearing assembly of Embodiment 4 of this utility model (the shaft is represented by dashed lines to show the hydrodynamic grooves on the inner circumferential surface of the bearing cavity). Detailed Implementation

[0033] In the description of this utility model, it should be noted that the terms "upper", "lower", "left", "right", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0034] For fluid dynamic pressure shaft cores and bearings, they are usually used together, with at least one of them having a fluid dynamic pressure groove. In this invention, by cleverly designing the traditional inclined groove into a multi-branched microchannel, a fluid dynamic pressure groove for rapid pressure build-up is obtained to achieve rapid pressure build-up.

[0035] The rapid pressure-building fluid dynamic pressure channel includes several sets of V-shaped dynamic pressure channels arranged around the perimeter. Each set of V-shaped dynamic pressure channels includes two inclined channels that intersect to form a V shape. The intersection point of the two inclined channels in each set of V-shaped dynamic pressure channels serves as the pressure-building center point. The inclined channel has at least two branch channels and an acceleration channel. The flow starting points of the two branch channels are separated from each other and extend towards the pressure-building center point, so that the flow ending points of the two branch channels converge and connect to the flow starting point of the acceleration channel, which extends towards the pressure-building center point.

[0036] as well as:

[0037] A fluid dynamic pressure shaft is provided, including a shaft body, wherein a dynamic pressure groove region is recessed on the outer peripheral surface of the shaft body, and the dynamic pressure groove region has the aforementioned fluid dynamic pressure groove for rapid pressure build-up.

[0038] A hydrodynamic bearing is provided, comprising a bearing body, wherein an axially penetrating inner cavity is formed within the bearing body, and a hydrodynamic groove region is provided on the inner circumferential surface of the inner cavity, wherein the hydrodynamic groove region has the aforementioned rapid pressure build-up hydrodynamic groove.

[0039] A shaft bearing assembly is provided, comprising a hydrodynamic bearing and a hydrodynamic shaft. The hydrodynamic bearing has an axially penetrating inner cavity, and the hydrodynamic shaft is located within the inner cavity. A hydrodynamic groove region is recessed on the outer circumferential surface of the hydrodynamic shaft, and the hydrodynamic groove region has the aforementioned rapid pressure-building hydrodynamic groove. The hydrodynamic bearing is fixed, while the hydrodynamic shaft rotates. The rotation direction of the hydrodynamic shaft is opposite to the flow pressure-building direction of the V-shaped hydrodynamic groove.

[0040] A shaft bearing assembly is provided, comprising a hydrodynamic bearing and a hydrodynamic shaft. The hydrodynamic bearing has an axially penetrating inner cavity, and the hydrodynamic shaft is located within the inner cavity. The inner circumferential surface of the inner cavity is provided with a hydrodynamic groove region, which has the aforementioned rapid pressure-building hydrodynamic groove. The hydrodynamic bearing is fixed, while the hydrodynamic shaft rotates. The rotation direction of the hydrodynamic shaft is the same as the flow pressure-building direction of the V-shaped hydrodynamic groove.

[0041] Please refer to Figures 1 to 7 As shown, an example is given where the hydrodynamic grooves are located on the outer circumferential surface of the hydrodynamic shaft core. illustrate.

[0042] A hydrodynamic shaft core includes a shaft core body 10, which is made of ceramic or metal, such as stainless steel. A hydrodynamic groove region is recessed on the outer circumferential surface of the shaft core body. The hydrodynamic groove region has several sets of V-shaped hydrodynamic grooves arranged circumferentially. Each set of V-shaped hydrodynamic grooves includes two intersecting inclined grooves forming a V shape. A ridge is formed between the inclined grooves of adjacent sets of V-shaped hydrodynamic grooves. The intersection point of the two inclined grooves in each set of V-shaped hydrodynamic grooves serves as the pressure-building center point. The pressure-building center points A of several sets of V-shaped hydrodynamic grooves in the same hydrodynamic groove region are all located on the same circumference. Preferably, the total number of all pressure-building center points O in the same hydrodynamic groove region is an odd number of 3 or more, and they are evenly spaced along the outer circumference of the shaft core body 10. This avoids the situation where multiple pressure-building center points A are radially aligned, which is beneficial for improving the radial suspension support force formed between the shaft core body 10 and the inner cavity of the bearing 20. The inclined channel has at least two branch channels and an acceleration channel. The flow initiation points of the two branch channels are separate and extend towards the pressure-building center point, such that the flow endpoints of the two branch channels converge at the flow initiation point of the acceleration channel. Preferably, the flow endpoints of the two branch channels converge at an acute angle, and the acceleration channel extends towards the pressure-building center point. The acceleration channel has an acceleration section that gradually narrows along the flow direction; the channel area at the beginning of the acceleration section is less than or equal to the sum of the channel areas at the flow endpoints of the two branch channels, and the channel area at the end of the acceleration section is less than the channel area at the beginning of the acceleration section. Upon entering the acceleration section, the flow velocity increases significantly.

[0043] like Figure 2 As shown, each inclined trench includes a branch trench 11, a branch trench 12, an acceleration trench 13, a branch trench 14, and an acceleration trench 15. The flow starting points of the branch trenches are arranged at intervals along the overall flow direction of the inclined trench. The oil from branch trenches 11 and 12 merges and connects to the flow starting point of the acceleration trench 13, where the oil velocity is accelerated for the first time. Then, it merges and connects with the oil from branch trench 14 to the flow starting point of the acceleration trench 15, where the oil velocity is accelerated for the second time. Therefore, from the perspective of the entire inclined trench, the oil velocity in all branch trenches 11, 12, 13, 14, and 15 flowing towards the pressure building center point A exhibits an increasingly faster acceleration trend. In this way, the oil velocities of the two inclined trenches converge under the acceleration trend to quickly build pressure at the pressure building center point A.

[0044] Combination Figures 3 to 5 As shown, the bearing 20 is fixed, while the hydrodynamic shaft 10 rotates; the rotation direction of the hydrodynamic shaft 10 is counterclockwise as indicated by the arrow. Therefore, the flow pressure build-up direction of the V-shaped hydrodynamic groove is clockwise. Figure 4 As shown, the oil in each inclined groove flows faster towards the pressure build-up center point A, as... Figure 5 As shown, the flow velocity in the direction away from the pressure building center point A will be blocked and become slower. Therefore, most of the oil accelerates and flows towards the pressure building center point A, effectively participating in pressure building, thereby achieving rapid pressure building and high pressure building.

[0045] Furthermore, such as Figure 2 As shown, a widened groove A1 extends from the pressure-building center point A toward the flared end of the V-shaped dynamic pressure groove. The two sides of the widened groove A1 maintain gaps with the two inclined grooves respectively. The shape of the widened groove A1 is not... Figure 2 The illustration is for illustrative purposes only. In actual design and manufacturing, the widened groove A1 can be omitted, or both sides of the widened groove A1 can be connected to the two inclined grooves respectively. For example... Figure 6 As shown, it can be used to illustrate the situation where the widened slot A1 is cancelled.

[0046] like Figure 7 As shown, each inclined groove includes a branch groove 11, a branch groove 12, an acceleration groove 13, a branch groove 14, and an acceleration groove 15. The oil in the branch grooves 11 and 12 merges and connects to the flow starting point of the acceleration groove 13, where the oil speed is accelerated for the first time. Then, the oil in the acceleration groove 13 merges and connects to the flow starting point of the acceleration groove 15, where the oil speed is accelerated for the second time. Compared to Embodiment 1, Embodiment 3 is equivalent to having auxiliary grooves 17 connected to both sides of the pressure-building center point in Embodiment 1. The flow starting points of the auxiliary grooves 17 are located on the outer side of the two inclined grooves, and the flow ending points of the auxiliary grooves 17 merge and connect with the pressure-building center point. Since a secondary pressure-building groove extends from the flared end of the V-shaped dynamic pressure groove away from the pressure-building center point, the flow ending point of the auxiliary grooves 17 merges with the pressure-building center point and extends and connects towards the secondary pressure-building groove, so that the pressure-building center point is set as the pre-pressure-building center point 16, and the secondary pressure-building groove becomes the effective pressure-building center point A'.

[0047] like Figure 3 As shown, the bearing has an axially penetrating inner cavity for mounting the shaft core. The inner cavity is smooth. The bearing is typically cylindrical or approximately cylindrical and is made of powder metallurgy or ceramic materials. The shaft core includes a shaft core body 10, which is located within the inner cavity of the bearing 20. In use, the bearing 20 is stationary, and the shaft core rotates within the inner cavity. The shaft core is a rapidly pressurizing hydrodynamic shaft core, and its rotation direction is opposite to the flow pressure direction of the V-shaped hydrodynamic groove. The hydrodynamic groove area on the shaft core body extends beyond both ends of the effective axial working length that mates with the inner cavity of the bearing. Figure 1As shown, the outer periphery of the shaft core body 10 is sequentially divided along the axial direction into a smooth surface area 101, a first dynamic pressure groove area 102, an annular groove 103, and a second dynamic pressure groove area 104. Typically, the smooth surface area 101, the first dynamic pressure groove area 102, and the second dynamic pressure groove area 104 have the same outer diameter, while the bottom outer diameter of the annular groove 103 is smaller. This creates a recessed area between the annular groove 103 and the inner cavity of the bearing 20, reducing friction between the shaft core and the bearing. The first dynamic pressure groove area 102 extends beyond one end of the inner cavity of the bearing 20, with a portion of the V-shaped dynamic pressure groove of the first dynamic pressure groove area 102 protruding from one end of the bearing's inner cavity. The second dynamic pressure groove area 104 extends beyond the other end of the inner cavity of the bearing 20, with a portion of the V-shaped dynamic pressure groove of the second dynamic pressure groove area 104 protruding from the other end of the bearing's inner cavity.

[0048] It should also be noted that, as mentioned above, bearing 20 is made of powder metallurgy materials or ceramic materials, etc. The aforementioned powder metallurgy materials also refer to porous metallic materials. These materials are made by pressing and sintering (same or different) metal powders, resulting in a porous structure with pores accounting for approximately 10%-35% of the volume. Before use, the bearing shell is immersed in hot oil for several hours to fill the pores with lubricating oil. The resulting bearing is called an oil-impregnated bearing, which has self-lubricating properties. In practical applications, the materials are not limited to powder metallurgy materials or ceramic materials. Non-metallic materials, such as plastics, rubber, and nylon, can also be used in hydrodynamic shafts under specific working conditions, such as when there are special requirements for noise reduction and corrosion resistance. It can also be metallic materials, such as: 1. Bearing alloys, also known as Babbitt metal, which contain tin and lead matrix, have good comprehensive performance but low mechanical strength, and can be cast onto steel or cast iron bearing bases; 2. Copper alloys, mainly tin bronze, aluminum bronze and lead bronze. Tin bronze is suitable for medium speed, medium load or heavy load conditions, aluminum bronze is suitable for low speed and heavy load conditions, and lead bronze is suitable for high speed and heavy load conditions; 3. Cast iron, which is a light load and low speed bearing material.

[0049] Furthermore, the shaft core body 10 is preferably made of metal materials such as ceramic or stainless steel. In practical applications, other materials can also be selected. The processing of the dynamic pressure groove area on the outer circumference of the shaft core body 10 can be carried out by laser processing (laser engraving), which can meet the requirements of different materials and processing dimensions. This makes it easy and feasible to process the relatively complex inclined grooves on the surface of the shaft core that imitate the Tesla microchannel principle. It is less difficult to process the grooves in the bearing cavity. It puts forward higher requirements for the shaft core bearing assembly to achieve rapid pressure build-up, stable pressure build-up and pressure maintenance with a simpler solution, which is directly related to the smoothness and reliability of rotation.

[0050] Please refer to Figures 8 to 9 As shown, the hydrodynamic grooves are set on the inner circumferential surface of the inner cavity of the hydrodynamic bearing. Examples are provided to illustrate the form.

[0051] A shaft bearing assembly is provided, comprising a hydrodynamic bearing and a hydrodynamic shaft core. The hydrodynamic shaft core includes a shaft core body 10, and the hydrodynamic bearing 20' includes a bearing body. An axially penetrating inner cavity is formed within the bearing body. The inner circumferential surface of the inner cavity is provided with a hydrodynamic groove region. The hydrodynamic groove region has the aforementioned rapid pressure-building hydrodynamic groove. The hydrodynamic groove can be a microchannel structure of any of the foregoing embodiments or a microchannel structure of more different embodiments obtained by simple variations / combinations. The hydrodynamic shaft core is located within the inner cavity. In use, the hydrodynamic bearing is fixed, while the hydrodynamic shaft core rotates. The rotation direction of the hydrodynamic shaft core is the same as the flow pressure-building direction of the V-shaped hydrodynamic groove. In this fourth embodiment, the inner circumferential surface of the inner cavity is provided with two axially spaced hydrodynamic groove regions 201, with a smooth surface region 202 between the two hydrodynamic groove regions 201. Furthermore, the outer circumferential surface of the shaft core body 10 is designed to be smooth.

[0052] The key design feature of this invention lies in its ingenious transformation of a traditional inclined groove into a multi-branched microchannel. This microchannel comprises at least two branch grooves and an acceleration groove. The flow initiation points of the two branch grooves are separate and extend towards the pressure-building center point. The flow endpoints of the two branch grooves converge and connect to the flow initiation point of the acceleration groove, which also extends towards the pressure-building center point. Thus, utilizing a Tesla-inspired microchannel principle, the inclined grooves on both sides gradually accelerate, thereby achieving rapid pressure building in each set of V-shaped dynamic pressure grooves and increasing the pressure build-up pressure.

[0053] The above description is merely a preferred embodiment of the present utility model and does not constitute any limitation on the technical scope of the present utility model. Therefore, any minor modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present utility model shall still fall within the scope of the technical solution of the present utility model.

Claims

1. A rapid pressure-building fluid dynamic pressure trench, comprising a plurality of sets of V-shaped dynamic pressure trenches arranged circumferentially, each set of V-shaped dynamic pressure trenches comprising two inclined trenches converging to form a V shape, the intersection point of the two inclined trenches in each set of V-shaped dynamic pressure trenches serving as the pressure-building center point; characterized in that: The inclined groove has at least two branch grooves and an acceleration groove. The flow starting points of the two branch grooves are separate from each other and extend toward the pressure building center point, so that the flow ending points of the two branch grooves converge and connect to the flow starting point of the acceleration groove, which extends toward the pressure building center point.

2. The rapid pressure-building fluid dynamic pressure trench according to claim 1, characterized in that: The pressure-building center point extends towards the flared end of the V-shaped dynamic pressure groove with a widened groove.

3. The rapid pressure-building fluid dynamic pressure trench according to claim 2, characterized in that: The widened groove maintains a gap between its two sides and the two inclined grooves respectively; Alternatively, the widened groove may be connected to two inclined grooves on both sides.

4. The rapid pressure-building fluid dynamic pressure trench according to claim 2, characterized in that: The acceleration trench has an acceleration section that gradually narrows along the flow direction; the trench area at the beginning of the acceleration section is less than or equal to the sum of the trench areas at the flow endpoints of the two branch trenches, and the trench area at the end of the acceleration section is less than the trench area at the beginning of the acceleration section.

5. The rapid pressure-building fluid dynamic pressure trench according to claim 1, characterized in that: Auxiliary channels are connected to both sides of the pressure-building center point. The flow starting point of the auxiliary channels is located outside the two inclined channels, and the flow ending point of the auxiliary channels merges and connects with the pressure-building center point.

6. The rapid pressure-building fluid dynamic pressure trench according to claim 5, characterized in that: A secondary pressure-building groove extends from the flared end of the V-shaped dynamic pressure groove away from the pressure-building center point. The flow endpoint of the auxiliary groove merges with the pressure-building center point and extends through the secondary pressure-building groove, so that the pressure-building center point is set as the pre-pressure-building center point, and the secondary pressure-building groove becomes the effective pressure-building center point.

7. The rapid pressure-building fluid dynamic pressure trench according to claim 1, characterized in that: The flow starting points of the branch trenches are arranged along the overall flow direction spacing of the inclined trenches.

8. A hydrodynamic shaft core, comprising a shaft core body, wherein a hydrodynamic groove region is recessed on the outer peripheral surface of the shaft core body, characterized in that: The dynamic pressure trench region has a rapid pressure-building fluid dynamic pressure trench as described in any one of claims 1 to 7.

9. A hydrodynamic bearing, comprising a bearing body, wherein an axially penetrating inner cavity is formed within the bearing body, and a hydrodynamic groove region is provided on the inner circumferential surface of the inner cavity, characterized in that: The dynamic pressure trench region has a rapid pressure-building fluid dynamic pressure trench as described in any one of claims 1 to 7.

10. A shaft bearing assembly, comprising a hydrodynamic bearing and a hydrodynamic shaft, wherein the hydrodynamic bearing has an axially penetrating inner cavity, and the hydrodynamic shaft is located within the inner cavity, characterized in that: The outer circumferential surface of the fluid dynamic pressure shaft core is recessed with a dynamic pressure groove area. The dynamic pressure groove area has a fluid dynamic pressure groove for rapid pressure building as described in any one of claims 1 to 7. The fluid dynamic pressure bearing is fixed, while the fluid dynamic pressure shaft core rotates. The rotation direction of the fluid dynamic pressure shaft core is opposite to the flow pressure building direction of the V-shaped dynamic pressure groove. Alternatively: the inner circumferential surface of the inner cavity is provided with a dynamic pressure groove area, the dynamic pressure groove area having a fluid dynamic pressure groove for rapid pressure building as described in any one of claims 1 to 7, the fluid dynamic pressure bearing is fixed, and the fluid dynamic pressure shaft core rotates; the rotation direction of the fluid dynamic pressure shaft core is the same as the flow pressure building direction of the V-shaped dynamic pressure groove.

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