Anisotropic spiral channel gradient traction self-transport cylindrical grinding head, grinding device and preparation process

Abstract

This invention discloses an anisotropic spiral flow channel gradient-driven self-contained cylindrical grinding head, grinding device, and manufacturing process. Several first anisotropic spiral flow channels are arranged along the circumferential direction on the end face of the grinding head, with a gradient gradually decreasing from the outer to the inner ring of the end face. At least one second anisotropic spiral flow channel is arranged on the side surface, with its width gradually decreasing from top to bottom along the axial direction. A spiral turning transition channel is provided at the junction of the side and end faces, connecting the second and first anisotropic spiral flow channels. This invention constructs a continuous anisotropic spiral flow channel structure on the side and end faces of the grinding head, forming an integrated grinding fluid transport path. It also introduces a synergistic driving mechanism of capillary pressure gradient, surface energy gradient, and structural guidance gradient to achieve stable centripetal transport of the grinding fluid in the anti-centrifugal direction under rotational conditions.

Description

Technical Field

[0001] This invention relates to the field of grinding processing and grinding equipment technology, and in particular to an anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head, grinding device and manufacturing process. Background Technology

[0002] Vertical face grinding, as an important precision machining method, is widely used in high-end manufacturing fields such as aerospace, precision molds, and advanced ceramics, playing a crucial role in achieving high surface quality and dimensional accuracy. However, under the condition of high-speed rotation of the grinding head, the grinding fluid is easily thrown off the grinding head surface under the action of strong centrifugal force. At the same time, the rotation-induced flow field forms a stable gas barrier layer near the grinding interface, significantly hindering the entry of grinding fluid into the grinding zone. This leads to deterioration of cooling and lubrication conditions in the grinding zone, resulting in a series of problems such as increased grinding temperature, increased grinding force, accelerated wear of the grinding wheel, and decreased workpiece surface quality.

[0003] To improve the fluid supply conditions in the grinding zone, existing technologies typically enhance cooling and lubrication effects by increasing the fluid supply flow rate, optimizing nozzle structure, adjusting the injection angle, or improving the fluid formulation. While these methods can alleviate thermal damage and clogging to some extent, the transport process of the grinding fluid, which mainly relies on external injection into the grinding zone, is still significantly constrained by the high-speed rotating flow field and centrifugal force. This generally results in problems such as low utilization rate, uncontrollable transport path, and difficulty in achieving directional fluid supply.

[0004] Meanwhile, existing grinding tools mostly employ uniform particle distribution or simple straight groove designs, with their structural functions primarily focused on chip containment and removal. They lack functional structures capable of actively regulating fluid behavior during grinding head rotation. Especially in vertical face grinding, the grinding head face and side surfaces act as a continuous interface, jointly participating in the transport and distribution of grinding fluid. However, existing technologies often design the face and side surfaces separately, failing to construct a synergistic flow guiding structure based on the overall flow path. Consequently, it is difficult to achieve continuous and stable transport of grinding fluid in three-dimensional space. This problem has become a key bottleneck restricting further improvements in grinding performance.

[0005] A search revealed a Chinese patent (application number 201880000382.4) that discloses a grinding wheel tool for microgrooving and its manufacturing method. The grinding wheel tool body is composed of multiple thin grinding wheels stacked along their thickness direction. Each thin grinding wheel has grooves of different widths on its outer edge, forming a self-dressing stable profile end face through differential wear. It can process microgrooves of various cross-sectional shapes such as V-shapes and U-shapes, and features high precision, low dressing requirements, and strong adaptability. However, the design of this patent focuses entirely on "maintaining the geometric profile" and "chip removal," making its groove function static and passive. It does not endow the grinding wheel with any ability to actively guide and deliver grinding fluid, failing to solve the fundamental problem of grinding fluid difficulty entering the grinding zone due to centrifugal force and air barriers under high-speed rotation. Therefore, it is deficient in active thermal management and enhanced cooling and lubrication.

[0006] Chinese patent (application number 202111462553.5) proposes a laser processing device and method for a grooved grinding wheel with a U-shaped cross-sectional profile. It employs an ultrafast laser combined with a reciprocating scanning path, and by controlling the laser offset spacing and the number of scanning cycles, it suppresses the problem of unilateral tilting, forming a bilaterally symmetrical U-shaped groove structure, significantly improving the grinding wheel's grinding stability and heat dissipation efficiency. However, fundamentally, the improvements in this patent are limited to the manufacturing process and the morphological optimization of the groove. The resulting U-shaped groove is essentially still a fixed, passive flow channel container; its coolant transport mechanism, which relies on external injection and fluid inertia, remains unchanged. This patent does not provide an active driving force to overcome centrifugal force and flow towards the center of the grinding zone when injecting grinding fluid, thus failing to achieve directional self-transportation of the grinding fluid.

[0007] Chinese patent (application number 202310357830.9) relates to a grinding wheel with linear cooling channels and its dual-wire 3D printing fabrication method. It uses dual-wire printing technology to precisely construct linear cooling channels within the working layer, combining a metal substrate and ceramic mold material to achieve efficient forming of the channel structure, effectively blocking heat transfer paths and enhancing coolant penetration and chip removal capabilities in the grinding zone. However, the core "linear cooling channel" of this patent is a simple straight line. Under high-speed rotation, this type of channel cannot guide the fluid centripetally; instead, centrifugal force causes the coolant to be thrown out in the middle of the channel, rendering its inherent "directional flow guidance" function ineffective. Therefore, this patent can be seen as using advanced technology to manufacture a traditional structure with limited functionality under rotation, failing to fully utilize the advantages of 2D printing in achieving efficient functional structures such as spatial spirals and gradient variable cross-sections.

[0008] Chinese patent (application number 202411486425.8) discloses an asymmetric trapezoidal turbulence structure spiral grooved grinding wheel. It features asymmetric trapezoidal turbulence units with their bottom edges fitted within a rectangular cross-section spiral groove. Utilizing the negative pressure suction effect generated by the high-speed rotation of the grinding wheel, it actively pushes the grinding fluid into the grinding arc zone, forming turbulent heat transfer and offering advantages such as noise reduction, vibration damping, and extended lifespan. However, the localized eddies and negative pressure effects relied upon in this patent's design are extremely unstable and have a limited range of influence, making it difficult to form a stable and uniform coolant film across the entire grinding arc zone. Furthermore, the turbulence structure introduced to generate turbulence significantly increases flow resistance, potentially severely weakening the overall flow rate. More importantly, the spiral grooves in this design primarily serve as carriers for the turbulence units, failing to effectively exert a dominant, global capillary pumping and guiding effect.

[0009] Chinese patent (application number 202510392575.0) discloses a cover plate cold carving grinding head, a processing method for the cold carving grinding head, and an application method. Structurally, this grinding head incorporates through-holes in the tool holder and tool head, and constructs cooling grooves and multiple cooling transverse grooves at the bottom of the tool head. This allows coolant to enter the grinding head through a central water outlet channel and be transported along the cooling hole-cooling groove-cooling transverse groove path to the grinding head and processing area, thereby achieving simultaneous cooling of the tool body and the workpiece. This significantly improves the problems of insufficient cooling capacity, severe tool wear, and poor processing stability in traditional cold carving grinding heads. However, the design of this patent is essentially still a passive cooling mode of "internal channel liquid supply + local overflow cooling." Its coolant transport path relies on external pressure, being transported to the tool head through the central channel and then diverted. While this structure improves cooling efficiency to some extent, the coolant flow direction is mainly dominated by pressure and inertia, lacking a dedicated control mechanism for centrifugal force and air barrier effects under rotating conditions, and thus failing to achieve active transport of grinding fluid to the center of the grinding area. Its cooling grooves only serve a distribution and guiding function, without constructing a continuous spatial guiding structure, thus failing to form a stable and controllable directional transport path on the grinding head surface. Furthermore, this structure does not consider the inhibitory effects of centrifugal force and air barrier on fluid adhesion and entry into the grinding zone under high-speed rotation conditions. The coolant still mainly passively diffuses or is thrown out radially, making it difficult to achieve continuous transport towards the center of the grinding zone. In addition, this patent does not introduce active driving mechanisms such as capillary pressure gradient, surface energy gradient, or structural anisotropy, therefore it cannot achieve self-driven, counter-centrifugal directional migration of the grinding fluid. Its cooling and lubrication functions are essentially still limited by traditional fluid supply methods, making it difficult to meet the high-efficiency and stable fluid supply requirements of high-speed precision grinding.

[0010] In summary, existing technologies, whether in terms of groove morphology optimization, manufacturing process improvement, or internal cooling channel design, have failed to build a continuous flow guiding system covering the end face and sides of the grinding head from the perspective of overall structural and functional integration. They have also failed to introduce an active mechanism that can drive the grinding fluid to migrate against centrifugal force under high-speed rotation conditions. Therefore, it is difficult to achieve stable and efficient transport of grinding fluid to the center of the grinding zone. Summary of the Invention

[0011] To address the technical problems existing in the prior art, this invention provides an anisotropic spiral flow channel gradient traction self-transporting cylindrical grinding head, grinding device, and manufacturing process; the grinding head end face and side face are designed as a unified functional interface in a collaborative structural system, a spatially continuous flow guiding structure is constructed on its surface, and combined with a multi-scale gradient driving mechanism, the grinding fluid can be autonomously transported from the outer edge to the central region along a predetermined path under high-speed rotation, thereby overcoming the limitations of centrifugal force and air barrier effect, and significantly improving the cooling and lubrication performance of the grinding zone.

[0012] To achieve the above objectives, the technical solution adopted by the present invention is as follows: In a first aspect, the present invention provides an anisotropic helical flow channel gradient traction self-contained cylindrical grinding head, comprising a substrate, the substrate including a side surface and an end surface, wherein a plurality of abrasive grains are arranged on the side surface and the end surface, and a plurality of first anisotropic helical flow channels arranged along the circumferential direction are provided on the end surface, the first anisotropic helical flow channels having a gradient change that gradually decreases from the outer circle to the inner circle of the end surface; at least one second anisotropic helical flow channel is provided on the side surface, the width of the second anisotropic helical flow channel gradually decreasing from top to bottom along the axial direction; a helical turning transition flow channel is provided at the junction of the side surface and the end surface, the helical turning transition flow channel being used to connect the second anisotropic helical flow channel and the first anisotropic helical flow channel; both the second anisotropic helical flow channel and the first anisotropic helical flow channel are provided with a superhydrophilic layer; the surface of the substrate is configured as a hydrophobic region, and the abrasive grains are configured as a superhydrophilic structure.

[0013] This invention constructs a continuous anisotropic spiral flow channel structure on the side and end face of the grinding head to form an integrated grinding fluid transport path. It also introduces a synergistic driving mechanism of capillary pressure gradient, surface energy gradient and structural guidance gradient to achieve stable centripetal transport of grinding fluid in the anti-centrifugal direction under rotating conditions. This effectively overcomes the limitations of air blockage and centrifugal fluid ejection, and significantly improves the fluid supply efficiency and cooling and lubrication performance of the grinding zone.

[0014] As a further technical solution, the trajectory equation of the first anisotropic helical flow channel is:

[0015] In the formula, x , yFor planar coordinates, φ Polar angle, r Polar radius, R o The initial radius of the outer edge of the grinding head end face is . b e The coefficient of end-face spiral contraction.

[0016] As a further technical solution, the trajectory equation of the second anisotropic spiral flow channel is:

[0017] In the formula, r Radial coordinates, θ Circumferential angle, z For axial coordinates, Ф For the spiral parameter variable, R o The outer radius of the grinding head. b s The coefficient of lateral spiral contraction. c s This is the axial pitch coefficient.

[0018] As a further technical solution, the width distribution of the first anisotropic spiral flow channel is as follows:

[0019] In the formula, w e ( r () represents the width of the flow channel at the lower end face. w e,max The maximum width of the outer edge. w e,min The minimum width of the inner edge. α For gradient exponent, r This is the current radius.

[0020] As a further technical solution, the width distribution of the second anisotropic spiral flow channel is as follows:

[0021] In the formula, w s ( z () represents the width of the side flow channel. w s,max This represents the maximum width of the upper side flow channel. λ s This is the side channel width contraction coefficient. z This refers to the axial position.

[0022] As a further technical solution, the optimal channel widths of the first anisotropic spiral channel and the second anisotropic spiral channel are as follows:

[0023] In the formula, w * Optimal minimum channel width ρ For cutting fluid density, ω This refers to the angular velocity of the grinding head.

[0024] As a further technical solution, the number of first anisotropic spiral channels and the number of second anisotropic spiral channels are determined according to the following formula:

[0025] In the formula, N For the number of flow channels, D The diameter of the grinding head. σ b The bending strength of the grinding head material. K s For safety reasons, F t The grinding force experienced by a single abrasive grain. d g The average particle size of the abrasive grains. Q This refers to the volumetric flow rate of the grinding fluid. v 液 The average flow velocity of the grinding fluid in the flow channel. H For flow channel depth, w max The maximum width of the flow channel. w min This is the minimum width of the flow channel.

[0026] As a further technical solution, the number of first anisotropic spiral channels and the spiral grooves of the second anisotropic spiral channel satisfy an arc-length relationship:

[0027] In the formula, d s Let d be the infinitesimal arc length of the spiral curve. r It represents a small change in the radial direction. r For the current radius, d φ It is a tiny angular change.

[0028] Secondly, the present invention provides a grinding apparatus, including the aforementioned anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head, and further including an ultrasonic electric spindle and a micro-lubrication device, as well as a multi-degree-of-freedom rotary manipulator; the ultrasonic electric spindle and the micro-lubrication device include an ultrasonic electric spindle, a nozzle, and an ultrasonic generator; wherein, the ultrasonic electric spindle is connected to the end of the multi-degree-of-freedom rotary manipulator, the ultrasonic electric spindle is connected to the aforementioned anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head, the ultrasonic generator controls the ultrasonic electric spindle, and a cutting fluid nozzle is provided on the side of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head.

[0029] Thirdly, the present invention provides a manufacturing process for an anisotropic helical flow channel gradient traction self-contained cylindrical grinding head, as follows: Preparation of matrix; An anisotropic spiral flow channel is formed on the end face of the substrate by photolithography-electrochemical etching, and a first anisotropic spiral flow channel and a second anisotropic spiral flow channel are formed on the side face of the substrate. A spiral turning transition flow channel is set at the junction of the side face and the end face of the substrate. The first anisotropic spiral flow channel, the second anisotropic spiral flow channel, and the spiral turning transition flow channel are treated to form a hydrophilic surface; Electroplated insulating varnish is applied to the grooves of the first anisotropic spiral flow channel, the second anisotropic spiral flow channel, and the spiral turning transition flow channel. Sand is applied to the end face and sides of the substrate to fix the abrasive on the end face of the substrate; Peel off the electroplated insulating varnish; The sides and end faces of the grinding head are subjected to composite electroplating to form a nickel substrate; A hydrophobic layer is formed on the nickel surface through surface chemical modification; The abrasive grains are treated to form a hydrophilic structure at one end.

[0030] Compared with the prior art, the advantages and positive effects of this invention are: (1) Highly efficient directional self-transportation capability integrating side and end faces. This invention breaks through the traditional design method of separating side and end face liquid supply, and constructs a continuous anisotropic spiral flow channel network, enabling the grinding fluid to achieve self-driven transport along a unified path of "axial transport from the side face - concentric convergence from the end face". The structure forms a three-dimensional self-transportation system of "continuous path - continuous gradient - directional constraint" as a whole, realizing integrated control of grinding fluid collection, transmission and central supply through a single flow channel, thereby significantly improving the continuity and stability of liquid supply.

[0031] (2) Side-end face synergistic force mechanism, anti-centrifugal fluid ejection and stable fluid locking capability. This invention provides a unified analysis of the force state of the grinding fluid on the side and end faces from the perspective of the overall system. In the side region, the geometric constraints and wettability gradient of the second anisotropic spiral flow channel enhance the fluid adhesion, making it less susceptible to being ejected by centrifugal force during axial transport. In the end face region, the centripetal spiral structure formed by the second anisotropic spiral flow channel works synergistically with the capillary pressure gradient to guide the fluid to continuously migrate towards the center. The side and end faces are coupled through a spiral turning transition flow channel, ensuring that the fluid is always within a controlled path, avoiding detachment or interruption in the transition area. At the same time, the microgroove structure, combined with surface tension, viscous resistance, and contact line pinning effect, forms multiple constraints on the fluid, significantly suppressing centrifugal fluid ejection, achieving stable locking and continuous supply of the grinding fluid, thereby effectively improving the lubrication and cooling effect and fluid utilization rate in the grinding zone.

[0032] (3) The coupling of transport, lubrication, and reinforcement comprehensively improves grinding performance. Based on the integrated self-transport structure, combined with ultrasonic assistance, the cavitation effect is used to improve the adsorption and transport capacity of grinding fluid in the flow channel, reduce flow resistance, and enhance the centripetal penetration capacity of the end face area. The ultrasonic action and the capillary drive of the spiral flow channel are superimposed to further enhance the overall transport efficiency, thereby effectively reducing the temperature of the grinding zone, suppressing grinding burns, and improving the machining quality. At the same time, the equal height structure design and high holding force coating can reduce the degree of wear and extend the tool life.

[0033] (4) Strong process controllability and versatility, with advantages of both green manufacturing and economic benefits. The side-end integrated structure of the present invention is compatible with mature manufacturing processes such as photolithography, electroplating, and ultrasonic modulation. By adjusting the flow channel geometry parameters and processing parameters, it can flexibly adapt to different grinding conditions (such as high speed, heavy load, and difficult-to-machine materials), and has good process controllability and engineering application versatility. At the same time, by constructing a continuous flow channel structure and a multi-gradient collaborative driving mechanism, it effectively overcomes the problems of air blockage and liquid resistance and centrifugal liquid slinging under high-speed rotation conditions, optimizes the grinding fluid transport path, significantly reduces the amount of coolant used, improves grinding efficiency and extends tool life, thereby reducing the overall production cost, and has both green manufacturing characteristics and significant economic benefits. Attached Figure Description

[0034] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0035] Figure 1 This is a three-dimensional schematic diagram of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head in Embodiment 1 of the present invention; Figure 2This is a side view of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head in Embodiment 1 of the present invention; Figure 3 This is a schematic diagram of the end face of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head in Embodiment 1 of the present invention; Figure 4 This is a force analysis diagram of the interface droplets on the side of the self-contained cylindrical grinding head in the gradient traction of the anisotropic spiral flow channel in Embodiment 1 of the present invention. Figure 5 This is a force analysis diagram of the interfacial droplets on the end face of the self-contained cylindrical grinding head in the gradient traction of the anisotropic spiral flow channel in Embodiment 1 of the present invention. Figure 6 This is a schematic diagram of the grinding device in Embodiment 2 of the present invention; Figure 7 This is a schematic diagram of the ultrasonic electric spindle and micro-lubrication device in Embodiment 2 of the present invention; Figure 8 This is a process flow diagram of the fabrication process of the anisotropic spiral flow channel gradient traction self-carrying cylindrical grinding head in Embodiment 1 of the present invention; Figure 9 This is a flow chart of the electroplating process for the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head in Embodiment 1 of the present invention. Figure 10 This is an exploded schematic diagram of the electroplating insulation device in Embodiment 1 of the present invention; Among them, Ⅰ-anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head, Ⅰ-1-upper end face, Ⅰ-2-tool holder, Ⅰ-3-second anisotropic spiral flow channel one, Ⅰ-4-second anisotropic spiral flow channel two, Ⅰ-5-side abrasive grains, Ⅰ-6-spiral turning transition flow channel, Ⅰ-7-first anisotropic spiral flow channel, Ⅰ-8-lower end face abrasive grains, Ⅰ-9-side matrix, Ⅰ-10-side droplets, Ⅰ-11-lower end face matrix, Ⅰ-12-lower end face droplets; II-Ultrasonic electric spindle and micro-lubrication device, II-1-Ultrasonic electric spindle, II-2-Cooling and film-forming mechanism, II-3-Ultrasonic generator, II-4-Cuter fluid reservoir, II-5-Ultrasonic vibrator, III-Multi-degree-of-freedom rotary robotic arm, IV-Upper end cover, V-Sleeve, VI-Sealing ring, VII-Tightening ring, VIII-Lower end cover, IX-Sealing cover, X-Mandrel. Detailed Implementation

[0036] It should be noted that the following detailed description is illustrative and intended to provide further explanation of the invention. Unless otherwise specified, all technical and scientific terms used in this invention have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains.

[0037] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, unless otherwise expressly indicated by the invention, the singular form is also intended to include the plural form. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof. For ease of description, the words "up," "down," "left," and "right" appearing in this invention only indicate that they are consistent with the up, down, left, and right directions of the accompanying drawings themselves, and do not limit the structure. They are merely for the purpose of facilitating the description of this invention and simplifying the description, and do not indicate or imply that the device or component 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 invention.

[0038] Definitions: The anisotropic spiral flow channel refers to a flow guiding structure that is spirally distributed along the surface of the grinding head and has directional differences in geometric dimensions, surface wettability, and spatial structure. Through the synergistic effect of cross-sectional gradient and surface energy gradient, it realizes the directional transport of grinding fluid along a predetermined direction under rotational conditions. Its "anisotropy" is mainly reflected in the following aspects: (1) Geometric anisotropy: The flow channel is continuously distributed along the spiral direction, and its cross-sectional dimensions (including width, depth or opening angle) change along the radial or flow direction, for example, forming a gradient structure of "wide outside-narrow inside" or "deep outside-shallow inside", thereby generating differentiated flow resistance and capillary pressure at different locations. (2) Surface anisotropy: The inner surface of the flow channel has different wetting properties or surface energy distribution in different regions. For example, wetting gradients are formed by material modification or micro / nano structure regulation, so that the fluid will have a directional spreading tendency in the flow channel. (3) Functional response anisotropy: Under rotational conditions, the flow channel exhibits different fluid transport capabilities in the clockwise and counterclockwise directions, causing the fluid to migrate preferentially along the preset direction (from the outer edge to the center) under the combined action; (4) Spatial distribution anisotropy: The flow channels are not only distributed on the end face of the grinding head, but also extend continuously along the side of the grinding head to form a three-dimensional spiral flow path that connects the end face and the side, so as to realize the coordinated transport of fluid on the overall surface.

[0039] Based on the aforementioned multi-scale anisotropic characteristics, this spiral flow channel can overcome the influence of centrifugal force generated by high-speed rotation under the multiple driving forces of capillary force, surface energy gradient and structure-induced pressure difference, and guide the grinding fluid to achieve directional and autonomous transport from the outer edge of the grinding head to the central region along the spiral path.

[0040] As described in the background section, existing technologies have shortcomings. To address these technical problems, this invention proposes an anisotropic spiral flow channel gradient-driven self-carrying cylindrical grinding head, grinding device, and manufacturing process. Addressing issues in existing vertical end-face grinding, such as difficulty in grinding fluid entering the grinding zone due to high-speed rotation, insufficient cooling and lubrication, high grinding temperature, and severe grinding wheel wear, this invention constructs a continuous anisotropic spiral flow channel structure on the side and end face of the cylindrical grinding head. This organically unifies axial transport on the side and radial convergence on the end face, forming an integrated liquid transport path. By constructing a geometric gradient that is "wider at the top and narrower at the bottom, wider on the outside and narrower on the inside," and synergistically introducing capillary pressure gradients, surface energy gradients, structural guidance gradients, and differences in abrasive grain-matrix wettability, stable centripetal self-driven transport of the grinding fluid is achieved along the anti-centrifugal direction under high-speed rotation conditions. Simultaneously, by combining ultrasonic vibration with a micro-lubrication system, the wettability and penetration of the grinding fluid are enhanced, effectively overcoming the problems of air blockage and centrifugal fluid ejection. This significantly improves the fluid supply efficiency and cooling and lubrication performance in the grinding zone, reduces grinding temperature and grinding force, and extends tool life. This invention has advantages such as strong self-transportation capability through a side-end face integrated system, high process controllability, and significant green manufacturing effects.

[0041] Example 1 In a typical embodiment of the present invention, such as Figure 1 As shown, an anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head is presented. An integrated continuous transport model of side and end face is established, revealing the directional migration mechanism of grinding fluid along the spiral path between the abrasive grain and the substrate interface. The flow channel geometry, interface wetting characteristics and fluid force behavior are coupled and analyzed to construct a multi-scale correlation system of "geometry-mechanics-materials-process". This provides a systematic theoretical basis and design method for the optimized design of anisotropic spiral flow channel grinding heads.

[0042] Specifically, the present invention includes the following key mechanisms: (1) Spatial path integrated coupling mechanism: The side and end face flow channels of the grinding head form a continuous spiral trajectory in space. The side flow channel transports the grinding fluid from the upper part of the grinding head to the lower end along the axis, and smoothly introduces it into the end face flow channel in the transition area; the end face flow channel further drives the liquid to converge radially towards the center. The two achieve seamless connection and flow continuity through the spiral turning transition flow channel, effectively avoiding the problems of fluid supply interruption or local stagnation in traditional structures, forming a three-dimensional continuous transport path of "upper → lower → inner".

[0043] (2) Continuous capillary pressure gradient driving mechanism: The overall flow channel exhibits a continuous contraction characteristic along the transport path: the side surface is "wider at the top and narrower at the bottom", and the end face is "wider at the outside and narrower at the inside". Essentially, it is unified as a geometric gradient that changes monotonically along the path, thereby establishing a continuous capillary pressure gradient throughout the entire path. This gradient drives the grinding fluid to continuously migrate from the high-level area on the side surface to the central area on the end face, achieving stable cross-interface transport, rather than a simple superposition of local driving.

[0044] (3) Synergistic enhancement mechanism of wettability gradient: The grinding head substrate adopts a superhydrophobic design, while the flow channel and abrasive grain region are superhydrophilic, forming a continuous wettability difference on the surface. This difference establishes a surface energy gradient on the flow channel path, driving the droplets to migrate directionally from the hydrophobic region to the hydrophilic region, achieving efficient liquid collection on the side and rapid spreading and convergence on the end face, thereby significantly improving the uniformity of liquid film coverage.

[0045] (4) Structural guidance and anisotropic constraint mechanism: The anisotropic spiral flow channel constructs a unified spatial flow guiding structure on the side and end faces, which effectively constrains the lateral diffusion of the liquid and confines the liquid within the preset spiral path. The side flow channel controls the transport rate through the axial pitch, and the end face flow channel adjusts the radial convergence capability through the spiral angle. The two work together to ensure that the liquid is continuously and stably transported to the center of the grinding zone under rotational conditions.

[0046] (5) Multi-parameter coupled optimization design mechanism: By introducing the competitive relationship between capillary force and centrifugal force and structural strength constraints, the flow channel design is transformed into a multi-parameter coupled optimization problem. The flow channel width depends on the balance between capillary driving force and centrifugal ejection tendency. The number of flow channels is determined by the effective bearing area and dimensions. At the same time, there is an optimal range for the width-to-depth ratio of the flow channels to coordinate the relationship between capillary driving capacity and flow resistance, so as to achieve unified optimization of liquid supply performance and structural strength.

[0047] The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head I is described in detail with reference to the accompanying drawings.

[0048] See Figure 1 and Figure 2 as well as Figure 3An anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head I comprises: an upper end surface substrate I-1, a tool holder I-2, a second anisotropic spiral flow channel I-3, a second anisotropic spiral flow channel II I-4, side abrasive particles I-5, a spiral turning transition flow channel I-6, a first anisotropic spiral flow channel I-7, lower end surface abrasive particles I-8, a side surface substrate I-9, and a lower end surface substrate I-11. Among these, the side abrasive particles I-5, the lower end surface abrasive particles I-8, the second anisotropic spiral flow channel I-3, the second anisotropic spiral flow channel II I-4, the spiral turning transition flow channel I-6, and the first anisotropic spiral flow channel I-7 are all superhydrophilic. The side surface substrate I-9 and the lower end surface substrate I-11 are both superhydrophobic, and the side abrasive particles I-5 and the lower end surface abrasive particles I-8 are fixed thereon, respectively. The abrasive grains I-5 on the side and I-8 on the lower end face are connected to the side substrate I-9 and the lower end substrate I-11 on one end of their axial direction, respectively, and the other end is a hydrophilic structure.

[0049] The second anisotropic spiral channel I-3 and the second anisotropic spiral channel II-4 are both anisotropic spiral channels. The first anisotropic spiral channel I-7 is an anisotropic spiral channel that is "wider on the outside and narrower on the inside" (i.e., the microscale spiral grooves gradually narrow from the outer periphery of the end face to the center). The spiral turning transition channel I-6 connects the second anisotropic spiral channel I-3, the second anisotropic spiral channel II-4, and the first anisotropic spiral channel I-7. The second anisotropic spiral channel I-3 and the second anisotropic spiral channel II-4 are axially symmetrically distributed along the side substrate I-9.

[0050] It should be noted that the second anisotropic spiral channel I-3 and the second anisotropic spiral channel II-4, as well as the first anisotropic spiral channel I-7, which are connected to the spiral turning transition channel I-6 and opened from the upper end face substrate I-1 along the side surface substrate I-9, all adopt anisotropic spiral channel gradient structure. Through the change of structural curvature, a pressure gradient is generated, which guides the liquid from the side to the end face under the combined action of geometric constraints and pressure gradient, and then guides it from the periphery of the end face to the central region, thereby overcoming the centrifugal liquid throwing phenomenon and realizing directional self-transportation.

[0051] In this embodiment, the side substrate I-9 and the lower end substrate I-11 are treated with a hydrophobic substrate process, making the superhydrophobic layer on the outside of the substrate a hydrophobic region. The side abrasive I-5, the lower end abrasive I-8, the second anisotropic spiral channel I-3, the second anisotropic spiral channel I-4, and the first anisotropic spiral channel I-7 are all treated with a hydrophilic process, making the ends of the abrasive particles and the channels hydrophilic regions. When droplets come into contact with the hydrophilic regions, they are adsorbed, causing the droplets in the hydrophilic regions to grow rapidly and play a role in water collection. Together with the side substrate I-9 and the lower end substrate I-11 with superhydrophobic layers, they guide water from the hydrophobic regions to the hydrophilic regions, improving cooling and lubrication efficiency.

[0052] Furthermore, it should be noted that the number of second anisotropic spiral channels is designed according to the following formula. The accompanying drawings of this embodiment only use two examples for illustration.

[0053] The self-transportation principle of grinding fluid within the integrated spiral flow channel groove on both the side and end faces is as follows: 1. Side-end integrated spiral flow channel trajectory model An anisotropic spiral flow channel is essentially a three-dimensional continuous spiral transport path that is "from top to bottom and from outside to inside": the side section, through the coupling effect of axial advancement and centripetal contraction, guides the liquid to converge towards the center while realizing the axial transport of the liquid from top to bottom; then, the spiral turning transition flow channel connects the side section flow channel and the end section flow channel; then, the end section turns into a pure centripetal planar spiral, which ultimately guides the fluid from the periphery to the grinding center, forming the terminal convergence link that determines the liquid supply efficiency.

[0054] 1.1 Trajectory Equations of Side-Mounted Helical Flow Channels (Second Anisotropic Helical Flow Channel I and Second Anisotropic Helical Flow Channel II) (1) In the formula, r For radial coordinates (m). θ Circumferential angle (rad) z Here is the axial coordinate (m). Ф For the spiral parameter variable (rad). R o Let be the outer radius of the grinding head (m). b s The lateral spiral contraction coefficient (centripetal strength) (rad) -1 ), c s The axial pitch coefficient (controlling the upward and downward propulsion) (m·rad) -1 ).

[0055] Formula (1) is used to describe the spatial trajectory of the side channel and to control the flow behavior through geometric parameters: when bs increases, the centripetal transport of the fluid is enhanced, which is essentially the strengthening of capillary drive; while when cs increases, the axial transport capacity of the fluid is mainly improved. Therefore, this spatial trajectory design is regarded as the "geometric root of the system's axial self-transport capacity".

[0056] 1.2 Trajectory Equation of Lower End Face Helical Flow Channel (First Anisotropic Helical Flow Channel) (2) In the formula, x , y For plane coordinates (m). φ It is the polar angle (rad). r The polar radius is (m). R o Let be the initial radius (m) of the outer edge of the grinding head end face. b e The end face helical contraction coefficient (rad) -1 ).

[0057] The core function and significance of formula (2) lies in describing the path of the liquid converging towards the grinding center. It directly determines whether the fluid can smoothly enter the grinding contact area, and is therefore regarded as the "core geometric factor of the lower end face liquid supply capacity".

[0058] 2. Variations in the curvature of the groove width generate capillary pressure gradients. In the anisotropic spiral channel grooves on the entire surface (including the side and end faces) of the anisotropic spiral channel self-contained cylindrical grinding head, the liquid exists in the form of a gas-liquid interface with curvature. When the width, curvature, or wettability of the channel groove changes along the spiral path, it causes a spatial change in the interface curvature, resulting in a capillary pressure difference. According to the Young-Laplace equation, the pressure relationship at the gas-liquid interface is as follows: (3) In the formula, P l The pressure is the liquid phase pressure (Pa). P g The pressure is the gas phase pressure (Pa). P c Capillary pressure (Pa).

[0059] The capillary pressure generated by the surface tension of a liquid at a curved interface is (4) In the formula, P c Capillary pressure (Pa), γThe surface tension of the droplet (N / m) θ * The apparent contact angle, r c The equivalent radius of curvature (equivalent capillary radius) of the microgroove.

[0060] As can be seen from the above formula, the radius of the second anisotropic spiral channel I-3 and the second anisotropic spiral channel II-4 gradually decreases from top to bottom along the side matrix I-9, and the curvature changes, thus forming a capillary pressure gradient.

[0061] The first anisotropic spiral flow channel I-7 gradually narrows from the periphery to the center along the lower end surface of the substrate I-11: the outer side has a large radius of curvature and low capillary pressure; the inner side has a small radius of curvature and high capillary pressure. This creates a capillary pressure gradient.

[0062] like Figure 1 As shown, the second anisotropic spiral channel I-3 and the second anisotropic spiral channel I-4 gradually narrow from top to bottom, while the first anisotropic spiral channel I-7 gradually narrows from the outer periphery to the center, with the center of the first anisotropic spiral channel I-7 being the narrowest. Therefore, the overall condition satisfies: (5) In the formula, P c,upper The capillary pressure (Pa) on the upper side is the pressure at the side. P c,lower The lower side capillary pressure (Pa) is the pressure at the side. P c,center Capillary pressure at the center of the end face (Pa), P c,edge The capillary pressure (Pa) is at the edge of the end face. Therefore, a capillary pressure gradient is formed from the upper part of the side to the lower part of the side, and from the periphery to the center.

[0063] Therefore, the corresponding liquid phase pressure is (6) In the formula, P l,upper The pressure of the liquid phase on the upper side (Pa). P l,lower The pressure of the liquid phase at the lower side (Pa) P l,edge Liquid phase pressure at the end face edge (Pa) and P l,edge This represents the liquid pressure at the center of the end face (Pa). It illustrates the liquid pressure along the side and end face paths. sThe pressure gradually decreases, creating a liquid pressure gradient from top to bottom and from the periphery to the center. This results in a high pressure at the top, a low pressure at the bottom, a high pressure at the periphery, and a low pressure at the center. Consequently, the liquid undergoes stable centripetal transport along the spiral flow channel across the entire surface.

[0064] Capillary pressure difference is converted into overall liquid pressure gradient: When the surface curvature or wetting conditions change P c This creates spatial variations, resulting in a liquid phase pressure gradient. Due to the gas phase pressure... P g In microscale flows, it is usually approximated as a constant, therefore, (7) This demonstrates that spatial changes in capillary pressure are directly converted into pressure gradients within the liquid. Consequently, the anisotropic spiral flow channel gradient pulls the self-contained cylindrical grinding head along anisotropic spiral paths on its entire surface, spontaneously transporting the material from top to bottom and then to the center.

[0065] 3. Flow channel width gradient model 3.1 Width distribution of the side flow channel (second anisotropic spiral flow channel) (8) In the formula, w s ( z ) represents the width of the side flow channel (m). w s,max The maximum width (m) of the upper side flow channel. λ s The side channel width contraction coefficient (m) -1 ), z The axial position is (m).

[0066] The purpose of this formula is to create a "wider at the top and narrower at the bottom" geometric configuration, thereby generating a capillary pressure gradient and giving the system the ability to directionally absorb liquid, thus directly controlling "whether active liquid absorption can be achieved".

[0067] 3.2 Width distribution of the lower end face flow channel (first anisotropic spiral flow channel) (9) In the formula, w e ( r ) represents the width of the flow channel at the lower end face (m). w e,max The maximum width of the outer edge (m). w e,min The minimum width of the inner edge (m). α It is the gradient exponent (dimensionless). rThe current radius (m).

[0068] The formula creates a "wider outside, narrower inside" geometric feature, which effectively enhances the liquid accumulation effect towards the center, thereby directly controlling the central liquid supply capacity and overall cooling efficiency. It is a key factor in determining cooling performance.

[0069] 4. Channel width ratio and capillary pressure gradient The width scaling factor is: (10) In the formula, K w The ratio of the width of the widest to the narrowest point of the flow channel (dimensionless). K w >1), w max The maximum width of the flow channel (m). w min This is the minimum width of the flow channel (m).

[0070] The core function of this indicator is to quantify the "gradient strength," which directly determines the magnitude of capillary driving force and the level of flow resistance (flow resistance). Therefore, it is a key control parameter in structural design and performance optimization.

[0071] The capillary pressure difference is: (11) When the width ratio coefficient K w When it increases, although the capillary pressure difference Δ P c While increasing flow rate enhances flow, it also significantly increases flow resistance; conversely, if Kw is too small, although it promotes smooth flow, it leads to the loss of self-priming capability. The core contradiction lies in this: too small a value will cause the system to lose the power to actively absorb liquid, while too large a value will cause fluid stagnation and "jam." Therefore, in practical design, Kw is not necessarily better the larger it is or the smaller the better; rather, there exists an optimal range of values ​​that balances self-priming and flow.

[0072] 5. The optimal flow channel width is (12) In the formula, w * Optimal minimum channel width (m) ρ The density of the cutting fluid (kg / m³) ω The value is the angular velocity of the grinding head (rad / s).

[0073] The engineering significance of this formula lies in describing the essential relationship between capillary force and centrifugal force reaching a critical equilibrium. The design conclusion derived from this is: as the rotational speed or the outer radius of the grinding head increases,w * The surface tension must be reduced accordingly to maintain equilibrium, while an increase in surface tension allows for... w * Take the larger value. The core mechanism is that if the flow channel is too wide, the capillary force will be insufficient to counteract the centrifugal force, causing the liquid to be thrown out; if it is too narrow, the flow resistance will be too high, hindering the flow. Therefore, w * It is a critical dimension that represents the optimal solution for satisfying the dual requirements of "active liquid absorption and smooth flow".

[0074] 6. Directional transport within the spiral channel driven by liquid pressure gradient (combined transport of rotation and centripetal propulsion) Under laminar flow conditions within thin liquid films or microchannel trenches, Poiseuille's law holds: (13) In the formula, Q Volumetric flow rate (m3). W The width of the trench is (m). h The thickness of the liquid film is (m). μ The viscosity is the dynamic viscosity (Pa·s). P l The pressure is the liquid pressure (Pa). s The path (m) is along the spiral direction of the groove. Q >0 indicates that the direction of flow is opposite to the direction of path. s Consistent. Due to s Defined as flowing from the periphery to the center, therefore: the liquid flows from the periphery to the center along the trench. Within the trench, the liquid primarily flows along the trench axis. The flow direction is consistent with the direction of the pressure gradient, which is along the trench path. s Therefore, the liquid flow direction is always along the tangent of the groove. For helical grooves, the tangent direction is not purely radial or purely circumferential, but a combination of both.

[0075] Since the spiral channel groove has a spatial inclination angle, its flow direction can be decomposed into radial and circumferential components; let the angle between the spiral channel groove and the circumferential direction be the helix angle. β Therefore, the total flow Q It can be broken down into (14) In the formula: Q r Radial transport flow rate (the flow rate that actually enters the grinding zone). Q θ This refers to the circumferential flow (the part that flows in a circular pattern). As long as the helix angle βEven if it is not equal to 90°, there must be a radial component in the direction of the groove.

[0076] Therefore, the radial component represents the effective flow rate actually transported to the grinding zone: (15) This indicates that the liquid continues to move towards the center while rotating along the spiral path, achieving a composite transport mode of "rotation + centripetal".

[0077] If the groove is perfectly circular (annular groove), then: helix angle β =90°, at this time (16) Note: The liquid can only flow in circles and cannot enter the center.

[0078] 7. Number of flow channels N Relationship with grinding head size and material Circulation area requirements: (17) In the formula, N The number of flow channels (dimensionless). Q The volumetric flow rate of the grinding fluid is (m³ / s). v 液 The average flow velocity of the grinding fluid in the flow channel (m / s) is given. H The depth of the flow channel is (m).

[0079] Strength requirements: (18) In the formula, D The diameter of the grinding head is in meters (m). σ b The bending strength (Pa) of the grinding head material. K s The safety factor (dimensionless, taken as 1.5–2.0) is used. F t The grinding force (N) experienced by a single abrasive grain. d g The average particle size of the abrasive grains (unit: m).

[0080] Therefore, the number of flow channels N It should meet the following requirements: (19) In the above formula, the first term ensures that the total flow area of ​​the flow channels meets the grinding fluid flow requirements; the second term limits the number of flow channels based on the strength of the grinding head material to avoid structural weakening due to excessive flow channels. Finally, N is taken as the smaller of the two to balance lubrication and strength.

[0081] 8. The spiral grooves form an integral anisotropic flow channel. The spiral grooves on the entire surface of the grinding head form a distinct anisotropic structure: along the groove direction, the flow is smooth and the resistance is low; perpendicular to the groove direction, the flow needs to cross the groove wall and the resistance is high.

[0082] (1) Along the direction of the trench The liquid mainly flows inside the groove, where the resistance is small, and it exhibits thin-film flow that satisfies Poiseuille's law, as shown in equation (13). Therefore, the liquid easily moves along the groove.

[0083] (2) Crossing the trench direction The liquid needs to overcome the surface tension or wetting barrier by flowing over the trench wall, resulting in a significant increase in flow resistance. Therefore: (20) In the formula, K parallel Permeability along the trench direction, K perpendicular This represents the permeability along the vertical direction of the groove. This is an anisotropic flow channel.

[0084] Therefore, this structure confines the liquid flow within a helical path, suppresses lateral diffusion, and enables directional transport.

[0085] 9. The overall strengthening effect of spiral flow channel groove structure on transport The spiral groove satisfies the arc length relationship: (twenty one) In the formula, d s Let d be the infinitesimal arc length (m) of the spiral curve. r It represents a tiny change (m) in the radial direction. r For the current radius (m), d φ For a small angular change (rad).

[0086] Spiral path d s Significantly larger than the radial path d r The spiral structure can extend the pressure gradient action distance, provide a continuous flow path, prevent the liquid from being interrupted due to radial abrupt changes, and thus form a stable centripetal liquid supply channel.

[0087] Under rotational conditions, the following must be satisfied: (twenty two) In the formula: P l Liquid pressure (Pa), ρ The density of the liquid is (kg / m³). ω The angular velocity of the grinding head is rad / s. rLet be the radius (m) of the droplet from the center of rotation. Centripetal transport requires that the capillary pressure gradient be greater than the centrifugal pressure gradient to ensure stable centripetal transport of the liquid.

[0088] As shown in the above equation, the larger the radius of the anisotropic helical flow channel self-contained cylindrical grinding head and the faster it rotates, the greater the outward pressure gradient. This will push the liquid outward. In the case of microscale grooves, the capillary pressure can often be on the same order of magnitude as or even greater than the centrifugal pressure. This means that the grooved helical structure can stably transport the liquid to the center.

[0089] In summary, anisotropic flow exhibits a capillary pressure gradient: narrow at the periphery and center, creating a capillary pressure difference. Helical flow guidance: the helical direction has a radial component, causing the liquid to continuously propel itself towards the center while circling. Anisotropic flow channels: make it easier for the liquid to flow along the channels rather than diffuse laterally. Therefore, the flow is "locked" onto the helical path, promoting centripetal transport. If the surface lacks anisotropic structure, the liquid will spread freely and be ejected during rotation. However, in a spiral groove, the groove walls create lateral constraints, and the flow is primarily along the groove direction. Therefore, centrifugal force mainly alters the pressure distribution without causing the liquid to detach from the groove.

[0090] The principle of self-transportation of grinding fluid between abrasive grains and the substrate: like Figure 4 and Figure 5 As shown, within the abrasive grain region of the entire surface (including the side and end faces) of the anisotropic helical flow channel gradient-driven self-contained cylindrical grinding head, the droplets are subjected to the coupling effects of multiple forces during transport: (twenty three) In the formula, F c For centrifugal force, F g For gravity, F p For pinning resistance, F s Viscous resistance, F σ Surface tension.

[0091] During the rotation of an anisotropic helical flow channel gradient-driven self-contained cylindrical grinding head, the stable retention of droplets on the grinding head surface is determined by the coupling effect of three types of forces: driving force, constraint force, and resistance force. The high-speed rotation of the grinding head generates a centrifugal field, subjecting the droplets to centrifugal force. Simultaneously, the droplets' own gravity also promotes their detachment from the grinding head surface. Therefore, centrifugal force and gravity constitute the main driving forces for droplet detachment from the grinding head. On the other hand, the surface tension of the droplets provides a contractile constraint force through the three-phase contact line, while the viscous drag and abrasive pinning drag generated during droplet flow on the surface impede droplet motion.

[0092] 1. Abrasive pinning resistance: (1) Elastic contact force of abrasive particles: When a droplet moves on the surface of a rotating grinding head, it interacts with the abrasive grains. The abrasive grains pin the droplet's three-phase contact line, thus hindering the droplet's movement. This interaction is essentially a contact mechanics behavior between the droplet and the abrasive grains, mainly involving two mechanisms: first, the pinning effect caused by the elastic deformation of the abrasive grain tip; and second, the interfacial adhesion effect generated when the droplet spreads along the side of the abrasive grain.

[0093] When a droplet contacts the tip of an abrasive grain, the surface tension of the droplet causes a slight elastic deformation at the grain tip (i.e., the droplet exerts a slight indentation on the abrasive grain), generating an elastic restoring force. This reaction force hinders the movement of the three-phase contact line of the droplet. Simultaneously, as the droplet spreads along the side of the abrasive grain, the adhesive force at the liquid-solid interface (adhesion derived from surface tension) also hinders the slippage of the contact line. Furthermore, the cone angle of the abrasive grain... α This will change the direction of the contact force, thus affecting the component of the pinning force in the direction of droplet motion.

[0094] Since abrasive grains are hard solids and droplets are fluids, contact deformation is mainly dominated by the elastic response of the abrasive grains. Therefore, the JKR (Johnson-Kendall-Roberts) contact model can be used to describe this process. This model is applicable to soft-hard contact systems and can simultaneously consider the coupling effect of elastic deformation and surface energy.

[0095] The JKR model posits that elastic deformation occurs at the contact area when two objects come into contact. The droplet exerts a squeezing effect on the abrasive grains, causing them to undergo minute elastic deformation and generating a corresponding elastic restoring force. According to Hertzian contact theory, when two objects are in elastic contact, the elastic contact force... F H Deformation of the object δ The relationship can be represented as: (twenty four) In the formula, E * It is the equivalent elastic modulus of droplets and abrasive grains. r p The radius of curvature of the abrasive grain tip. δ The amount of elastic deformation of the abrasive grain due to contact (the depth of the droplet penetrating the abrasive grain).

[0096] In addition to elastic contact forces, there is also adhesion between abrasive grains and droplets caused by surface energy. This adhesion force originates from the interaction between molecules at the liquid-solid interface, and its expression is: (25) In the formula, γ For liquid surface tension, r p The radius of curvature of the abrasive grain tip is denoted as .

[0097] Therefore, the pinning resistance of a single abrasive grain to a droplet can be expressed as the resultant force of elastic contact force and interfacial adhesion force: (26) (2) Total pinning resistance experienced by the droplet: When a droplet comes into contact with multiple abrasive grains, the total pinning resistance is the sum of the tangential components of the pinning forces of each abrasive grain in the direction of droplet motion, that is: (27) In the formula, N n This represents the number of abrasive particles in contact with the droplet. α It represents the cone angle of the abrasive grain.

[0098] (3) Mechanism of helical grooves enhancing pinning resistance The spiral groove structure can enhance the droplet pinning effect in the following two ways: 1) Increase the length of the three-phase contact wire The spiral grooves extend continuously along the circumference, allowing the droplets to form a longer three-phase contact line with the solid surface during the spreading process, thereby increasing the adhesion between the droplets and the grinding head surface.

[0099] 2) Change the direction of droplet motion The direction of droplet movement on the surface of a rotary grinding head is usually radial or tangential, while the direction of the helical grooves is inconsistent with the direction of droplet movement. This difference in direction increases the interfacial resistance during droplet movement, making it more difficult for the droplet to slip radially.

[0100] Therefore, the spiral groove structure significantly enhances the pinning resistance of the droplet by increasing the length of the three-phase contact line and changing the droplet's motion path, thereby improving the stability of the droplet under high-speed rotation conditions and inhibiting the droplet from being thrown out by centrifugal force.

[0101] 2. Centrifugal force: As the grinding head rotates, the anisotropic spiral flow channel gradient pulls the droplets from the side of the conveying cylindrical grinding head into a circular motion, and they are subjected to a centrifugal force pointing radially outward. F c The direction is radially perpendicular to the axis of rotation. z Outward, this centrifugal force can be decomposed into the direction of droplet motion ( x (Direction) to analyze its driving effect.

[0102] The radial distance from the droplet to the axis of rotation is (28) In the formula, r The radius of the grinding head is [value].

[0103] The centrifugal acceleration of the droplet is (29) Droplets on the surface of the grinding head typically take the shape of a spherical cap, and their volume can be approximated as... The droplets are symmetrically distributed in a spherical cap shape on the surface of the grinding wheel. A simplified analysis of the spherical cap droplets is performed, including the droplet height. H ~ R Therefore, the droplet volume V Approximately: (30) In the formula, R Let the effective radius of the droplet be 1. H This represents the droplet height.

[0104] Therefore, the centrifugal force experienced by the droplet is (31) In the formula, ρ The density is the liquid density.

[0105] The effect of spiral grooves on centrifugal force The helical grooves do not change the magnitude of the centrifugal force, but they do change the droplet's path. The centrifugal force of a droplet on the side is originally radial outward, but the helical grooves guide the droplet to move along the helical path, causing part of the centrifugal force to be converted into a helical tangential force.

[0106] As a droplet moves along the spiral groove, its trajectory changes from a radial straight line to a spiral curve, decomposing the centrifugal force into a tangential component along the spiral direction, thus reducing the effective radial component of the centrifugal force. Therefore, the spiral groove can reduce the tendency for the droplet to be directly ejected, which is beneficial for the stable transport of the droplet along the groove.

[0107] 3. Gravity: The droplet is also subject to its own gravity: (32) The effect of spiral grooves on gravity Spiral grooves reduce the effective component of gravity in the actual direction of droplet motion by altering the droplet's direction of movement, causing it to move along an oblique or spiral path. Although gravity itself remains unchanged, its direct driving effect on droplet slippage is weakened.

[0108] 4. Surface tension: The stability of the droplet on the grinding head surface is mainly controlled by the surface tension of the gas-liquid-solid three-phase interface. Under static conditions, the surface tension satisfies Young's equation. (33) In the formula, γ SG For solid-gas interface energy, γ SL For solid-liquid interface energy, γ LG For liquid-gas surface tension, θ r This is the static contact angle of the droplet.

[0109] When at rest, the droplet maintains a stable contact angle. θ r Surface tension generates an inward contraction force along the three-phase contact line. As the grinding head rotates, centrifugal force stretches the droplet, and the contact angle changes from the retraction angle... θ r Increase to dynamic advance angle θ a This causes a change in the radial component of the surface tension.

[0110] The three-dimensional contact line between the droplet and the gradient traction of the anisotropic helical flow channel in the self-contained cylindrical grinding head is an axisymmetric circle with a circumference of [missing information]. L =2π R The radial component of the static surface tension is: (34) The radial component of dynamic surface tension is (35) Therefore, as the grinding head rotates, the droplet experiences a net force of surface tension constraint. (36) In the formula, γ is the surface tension coefficient of the liquid-gas interface.

[0111] The effect of spiral grooves on surface tension Surface tension acts along the contact line towards the interior of the droplet, and its resultant force is proportional to the length of the contact line; the spiral grooves, by forming groove walls along the spiral direction, significantly increase the length of the three-phase contact line between the droplet and the solid. L Therefore, helical grooves can extend the contact line and guide the droplet's movement along the helical direction. The groove direction guides the droplet's centripetal flow, causing surface tension to effectively propel the liquid along the helical direction. This enhances droplet stability and promotes improved centripetal transport efficiency.

[0112] 5. Viscous resistance As a droplet expands on the surface of the grinding head, it forms a micron-sized liquid film between the droplet and the solid surface. The velocity gradient within the liquid film generates viscous shear force, thus creating resistance to the droplet's motion.

[0113] On the surface of a micro-grinding head, droplet flow typically satisfies a low Reynolds number condition: (37) In the formula, ρ For droplet density, μ This refers to dynamic viscosity. R e <<1), at this time, the characteristic deformation rate of the velocity distribution can be dominated by the radial expansion rate of the droplet.

[0114] When a droplet moves, its flow is dominated by viscous forces, while the inertial force is much smaller than the viscous force. Based on axisymmetric simplification, the characteristic deformation of a droplet is its radial characteristic radius. R ( t ), that is, the droplet contact line expansion rate: (38) Therefore, the flow is dominated by viscous forces (Stokes flow hypothesis), and the velocity distribution of the fluid element is approximately linear shear, that is, at the polar axis, there is no relative slippage between the droplet and the grinding head surface, and the velocity is... v =0, at the edge of the droplet the droplet's velocity and expansion rate are synchronized, at this time v = R Characteristic velocity gradient: (39) The surface of an abrasive grain can be considered as a partially slip boundary. Due to the micro-rough structure of the abrasive grain surface, a certain degree of slip effect occurs when the liquid flows on its surface. This behavior can be described using Navier slip boundary conditions: (40) In the formula, b The equivalent slip length is closely related to the micro-roughness and surface structure characteristics of the abrasive grain. When a droplet expands radially on the abrasive grain surface, the flow of the liquid film around the abrasive grain can be approximated as axisymmetric radial flow. Within the abrasive grain contact region (0 < 0 < 0), the slip length is approximately 1.5%. r < a ,in a (Equivalent contact radius of the contact area between the abrasive tip and the liquid film), with the liquid film thickness ranging from 0 to 1. z < h Within this region, the velocity distribution inside the liquid film satisfies the modified Poiseuille flow equation considering slip boundary conditions: (41) In the formula, z The coordinates are perpendicular to the surface of the abrasive grains. z = 0 represents the abrasive surface. z = h (Liquid-gas interface) According to Newton's law of internal friction, the viscous shear stress of a liquid film is: (42) Find the velocity distribution z The partial derivative is used to obtain the abrasive surface ( z Shear stress at (=0): (43) In the formula, μ Let be the dynamic viscosity. The viscous resistance of a single abrasive grain is the integral of the shear stress over the contact area. Assume the droplet forms a spherical cap on the tangential surface, and the contact line between the droplet and the inclined interface has a radius of . x The circle with area d S =2π x d x The viscous resistance experienced by a single abrasive grain is: (44) The total viscous resistance of the abrasive particles in the droplet-covered area is: (45) When the droplet is about to detach from the grinding head at the critical state, the driving force is less than or equal to the resultant force of the resistance and constraint forces.

[0115] The effect of helical grooves on viscous resistance Spiral grooves lengthen the flow path of droplets. (46) In the formula, d s d is the infinitesimal arc length (m) of the spiral curve. r It represents a small change (m) in the radial direction; r d is the current radius (m); φ For a small angular change (rad).

[0116] Spiral grooves increase d s Extending the capillary action distance mitigates the centrifugal effect. Simultaneously, it increases the contact area between the droplet and the solid surface, thereby improving liquid shear damping. Consequently, the droplet's flow velocity within the groove decreases, and the droplet is locked in for a longer period, which is beneficial for stable centripetal transport.

[0117] Droplet force model between abrasive grains and substrate in rotary grinding head When performing droplet force analysis on a high-speed rotating anisotropic helical flow channel gradient-driven self-contained cylindrical grinding head, a key principle needs to be clarified: The direction of pinning resistance is always opposite to the relative motion tendency of the droplet. Pinning resistance is not a fixed direction, but a passive resistance, and its direction depends on the direction of the droplet's sliding tendency under the action of external forces.

[0118] Viscous resistance is always opposite to the direction of the droplet's relative motion. Viscous resistance comes from: the viscosity of the liquid itself, and friction between the droplet and rough surfaces.

[0119] Surface tension points inward along the three-phase contact line, causing the droplet to contract. The surface tension acts on the three-phase contact line, and its overall effect is to contract the droplet, with the direction being from the contact line towards the center of the droplet.

[0120] like Figure 4 As shown, the force analysis of the interface between the side droplet I-10 and the substrate I-9 on the side of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head shows that the radially outward centrifugal force... F c Vertical downward gravity F g Inward and upward pinning resistance F p Inward and upward viscous resistance F s Surface tension pointing towards the center of the droplet F σ .

[0121] The conditions for a droplet to exist stably on the side surface of the grinding head are: (47) like Figure 5 As shown, the force analysis of the interface between the droplet I-12 on the lower end face of the self-contained cylindrical grinding head and the substrate I-11 in the anisotropic spiral flow channel gradient traction shows that the radially outward centrifugal force... F c Vertical downward gravity F g Radial inward pinning resistance F p radial inward viscous resistance F s Surface tension pointing towards the center of the droplet F σ .

[0122] The conditions for droplets to be transported from the periphery to the center on the end face of the grinding head are: (48) Example 2 In a typical embodiment of the present invention, such as Figure 6 and Figure 7 As shown, a grinding apparatus is provided to enhance the self-feeding effect of an anisotropic helical flow channel gradient traction self-feeding cylindrical grinding head. It includes: an anisotropic helical flow channel gradient traction self-feeding cylindrical grinding head I, an ultrasonic electric spindle and micro-lubrication device II, and a multi-degree-of-freedom rotary robotic arm III. This grinding apparatus can achieve multi-degree-of-freedom and ultrasonic machining.

[0123] The ultrasonic electric spindle and micro-lubrication device II includes: an ultrasonic electric spindle II-1, a parameter-controllable intelligent nozzle II-2, an ultrasonic generator II-3, a cutting fluid reservoir II-4, and an ultrasonic vibrating rod II-5. The ultrasonic electric spindle II-1, mounted on the multi-degree-of-freedom rotary robotic arm III, can achieve rotational ultrasonic vibration in all directions. The ultrasonic generator II-3 can control the relevant parameters of ultrasonic machining. The ultrasonic vibrating rod II-5 vibrates the grinding fluid in the cutting fluid reservoir II-4, achieving uniform distribution of the grinding fluid and enhancing lubrication and cooling effects. The grinding fluid is sprayed out through the parameter-controllable intelligent nozzle II-2.

[0124] The principle behind the improved wetting effect of adding an ultrasonic electric spindle and a micro-lubrication device to the grinding fluid in this example: According to the Linus Torvalds law, the wetting height hm of the grinding fluid without the addition of ultrasonic flux is: (49) In the formula, h m The height of liquid immersion (m). σ The surface tension of the liquid, θ Contact angle, ρ Liquid density (kg / m³) 3 ), g Acceleration due to gravity (m / s²) 2 ), r The width of the flow channel is in meters (m).

[0125] After the addition of ultrasound, the high-frequency, low-amplitude vibrations generated by the ultrasound produce a compression molding effect, under which the additional static pressure is: (50) In the formula, α 1 represents the extrusion die constant. u The speed of sound (m / s) A 0 represents the amplitude (dB) of the ultrasonic wave. d 0 represents the liquid level (m). This pressure acts directly on the liquid-solid interface, overcoming the contact angle hysteresis effect.

[0126] Height of wetting under extrusion molding effect h j As shown in the following formula: (51) Total wetting height of coolant after adding ultrasound h c for: (52) Under ultrasonic action, the total liquid wetting height is the sum of the original wetting height and the wetting height under the extrusion mold effect, which further improves the transport performance of the grinding fluid.

[0127] Ultrasonic cavitation includes the generation, expansion, oscillation, and collapse of cavitation bubbles. The energy released at the moment of cavitation bubble collapse is much greater than the grinding impact force, causing the flow field on the workpiece surface to change from laminar to turbulent, and the Reynolds number to increase significantly.

[0128] Nusselt number of fluid N u for (53) In the formula, R e Let Reynolds number be 1. P r is Prandtl's constant.

[0129] convective heat transfer coefficient of fluid h for (54) In the formula, k Thermal conductivity (W / (m×k)) L l denoted as the geometric length (m) of the heat transfer surface.

[0130] Therefore, an increase in the Reynolds number leads to an increase in the Nusselt number of the fluid, which in turn increases the convective heat transfer coefficient. Turbulence in the flow field increases the convective heat transfer coefficient, accelerates heat dissipation in the grinding zone, reduces liquid film viscosity, and thus reduces flow resistance.

[0131] In the helical flow channel of an anisotropic helical flow channel gradient-driven self-contained cylindrical grinding head, ultrasonic vibration produces two key effects: Radial component enhancement: The ultrasonic pressure wave generates a pressure gradient pointing towards the center within the helical flow channel, which superimposes in the same direction as the capillary pressure gradient. Path cleaning function: Cavitation effect prevents wear debris from clogging the flow channel and maintains unobstructed transport channels. Ultrasound increases the forward contact angle and decreases the backward contact angle of droplets in the flow channel, and reduces the contact angle hysteresis, making it easier for droplets to move centripetally along a spiral path.

[0132] Under high-speed rotation, centrifugal force attempts to throw the liquid out. Ultrasonic vibration counteracts centrifugal force through two mechanisms: increasing the adhesion work between the liquid film and the channel wall, and generating reverse hydrostatic support through the squeezing film effect.

[0133] In summary, this embodiment utilizes the physical field coupling effect generated by ultrasonic vibration to enhance wetting, improve the flow field, and increase net driving force, thereby achieving directional centripetal transport of grinding fluid along the spiral channel while resisting centrifugal interference. This solves the problem of traditional cylindrical grinding heads struggling to autonomously draw in fluid at high speeds, effectively eliminating the adverse effects of "air barriers" and "centrifugal fluid ejection" on lubrication and cooling in the grinding zone, and significantly enhancing the autonomous fluid supply performance of the anisotropic spiral channel gradient traction self-transporting cylindrical grinding head.

[0134] Example 3 In a typical embodiment of the present invention, such as Figure 8 and Figure 9 as well as Figure 10 As shown, a process for manufacturing an anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head is provided.

[0135] Specifically, such as Figure 8 As shown, the preparation process specifically includes the following steps.

[0136] First, based on Example 1, the spiral arrangement of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head on the end face and side is designed. The substrate is made of stainless steel and machined into a cylindrical structure with a diameter of 1–6 mm. First, the stainless steel is machined into a cylindrical grinding head of the required size using a turning process. Then, the end face and cylindrical side of the grinding head are polished to obtain a relatively smooth and clean surface. Subsequently, the machined substrate is ultrasonically cleaned to remove surface oil and impurities. The cleaning process is carried out sequentially in acetone, anhydrous ethanol, and deionized water to ensure a clean substrate surface, providing good surface conditions for subsequent abrasive grain arrangement and electroplating processes.

[0137] like Figure 9 As shown, an anisotropic spiral flow channel structure and a spiral turning transition channel are formed on the surfaces of the stainless steel side substrate I-9 and the lower end substrate I-11 by photolithography-electrochemical etching. Subsequently, the surfaces of the second anisotropic spiral flow channel I-3, the second anisotropic spiral flow channel I-4, and the first anisotropic spiral flow channel I-7 are subjected to oxygen plasma activation treatment to form a hydrophilic surface rich in hydroxyl groups. At the same time, a TiO2 nano-hydrophilic film is deposited on the flow channel surface by sol-gel method to further enhance the hydrophilicity and capillary transport capacity of the trench, thereby constructing a hydrophilic flow channel structure with directional liquid transport function.

[0138] The core function of applying electroplating insulating varnish only to the channel grooves, while cleaning the rest of the area, is to achieve selective electroplating: only the side substrate I-9 and the lower end substrate I-11 surfaces are exposed to the electroplating solution, while the groove area is isolated from the electrolyte due to the insulating varnish coverage. This ensures that the subsequent electroplating process only occurs on the side substrate I-9 and the lower end substrate I-11 surfaces, preventing abrasive particles from depositing in non-target areas. This special electroplating insulating varnish has advantages such as acid and alkali resistance, strong adhesion, no pollution, suitability for long-term immersion in the electroplating solution, and easy peeling after use.

[0139] After applying insulating varnish to the cylindrical end face, with the end face facing upwards, sand is applied to the end face by rotating the tool holder I-2. The sand application is performed using a combination of sand drop method and mechanical vibration. During operation, cubic boron nitride (CBN) abrasive grains or diamond abrasive grains are evenly sprinkled onto the surface of the substrate I-11 on the lower end face of the grinding head, and mechanical vibration with specific parameters is applied to form the lower end face abrasive grains I-8.

[0140] However, compared to the first anisotropic spiral flow channel I-7, which is gradient-driven from the lower end face of the conveyor cylindrical grinding head, and the second anisotropic spiral flow channels I-3, I-4, and I-6, which are gradient-driven from the side face of the conveyor cylindrical grinding head, there are significant differences in their overall structure, size, and the side substrate I-9 and lower end substrate I-11 that require sand coating. Therefore, the electroplating equipment required in the electroplating process also differs to some extent. For example... Figure 10 As shown, to ensure insulation of parts other than the cylindrical surface during sand planting, a dedicated electroplating insulation device was designed. Made of PVC material, it is not only resistant to electroplating solution corrosion, not easily deformed, and has good tightness, but is also simple to operate and easy to assemble and disassemble. By sequentially connecting and tightening the upper end cap IV, sleeve V, VI-sealing ring, and VII-tightening ring, the upper end face of the cylindrical grinding head, excluding the tool holder I-1, can be fixed. By sequentially connecting and tightening the lower end cap VIII, sealing cap IX, and mandrel X, the lower end face base I-11 of the cylindrical grinding head can be covered and fixed. Sand planting is still carried out using a combination of sand drop method and mechanical vibration. By rotating the tool holder I-2 horizontally, side abrasive particles I-5 are formed on the side base I-9 of the grinding head, excluding the second anisotropic spiral flow channel I-3, the second anisotropic spiral flow channel II-4, and the spiral turning transition flow channel I-6.

[0141] After the abrasive cluster sand-planting process is completed, the electroplated insulating varnish is peeled off after a period of time. At this time, the abrasive grains and the nickel plating layer have a certain bonding strength. However, in order to ensure the overall bonding strength of the abrasive grains on the surface of the grinding wheel, the entire grinding wheel needs to be composite electroplated after the electroplated insulating varnish is peeled off, until it is thickened to the predetermined thickness.

[0142] The composite electroplating process uses nickel as the base metal. Under energized conditions, nickel ions are reduced and deposited on the surface of the cathode (grinding wheel substrate), thereby firmly bonding the abrasive grains pre-arranged on the bosses to the substrate surface. The plating thickness must be precisely controlled during the process, reaching approximately 2 / 3 of the abrasive grain diameter. Maintaining this optimal thickness ensures both sufficient holding strength for the abrasive grains and excellent cutting performance.

[0143] Furthermore, a hydrophobic layer is formed on the nickel matrix through surface chemical modification, while the diamond abrasive surface retains its original properties without reaction. Fatty acids, such as myristic acid or stearic acid, can be used to modify the nickel surface. These fatty acids can react chemically with metallic nickel to form metal carboxylates, in the form: Ni + RCOOH → Ni(RCOO)2, thus forming a low-surface-energy organic hydrophobic layer on the nickel matrix surface. The diamond surface, due to its strong chemical inertness, does not react with the fatty acids and therefore retains its original hydrophilic properties. Through this selective reaction, the hydrophobic surface properties of the nickel matrix and the hydrophilic surface properties of the diamond abrasive can be separated within the same structure. The advantages of this method are its automatic selectivity, the absence of additional post-processing steps, and the ability to achieve stable surface functionalization using the inherent chemical properties of the material.

[0144] Furthermore, the hydrophobic layer on the surface of the abrasive grains can be selectively removed to restore their hydrophilicity.

[0145] Furthermore, the anisotropic spiral flow channel gradient traction self-feeding cylindrical grinding head was dynamically balanced until it met the requirements, thus completing the fabrication of the anisotropic spiral flow channel gradient traction self-feeding cylindrical grinding head.

[0146] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. An anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head, characterized in that, The system includes a substrate, which comprises side surfaces and end surfaces. A plurality of abrasive grains are arranged on the side surfaces and end surfaces. A plurality of first anisotropic spiral channels are provided on the end surfaces, arranged along a circumferential direction, with the first anisotropic spiral channels exhibiting a gradient that gradually decreases from the outer to the inner ring of the end surface. At least one second anisotropic spiral channel is provided on the side surfaces, with the width of the second anisotropic spiral channel gradually decreasing axially from top to bottom. A spiral turning transition channel is provided at the junction of the side surfaces and end surfaces, connecting the second anisotropic spiral channel and the first anisotropic spiral channel. Both the second and first anisotropic spiral channels are provided with a superhydrophilic layer. The substrate surface is configured as a hydrophobic region, and the abrasive grains are configured as a superhydrophilic structure.

2. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 1, characterized in that, The trajectory equation for the first anisotropic helical flow channel is: In the formula, x , y For planar coordinates, φ Polar angle, r Polar radius, R o The initial radius of the outer edge of the grinding head end face is . b e The coefficient of end-face spiral contraction.

3. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 2, characterized in that, The width distribution of the first anisotropic helical flow channel is as follows: In the formula, w e ( r () represents the width of the flow channel at the lower end face. w e,max The maximum width of the outer edge. w e,min The minimum width of the inner edge. α For gradient exponent, r This is the current radius.

4. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 1, characterized in that, The trajectory equation for the second anisotropic helical flow channel is: In the formula, r Radial coordinates, θ Circumferential angle, z For axial coordinates, Ф For the spiral parameter variable, R o The outer radius of the grinding head. b s The coefficient of lateral spiral contraction. c s This is the axial pitch coefficient.

5. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 1, characterized in that, Width distribution of the second anisotropic helical flow channel: (8) In the formula, w s ( z () represents the width of the side flow channel. w s,max This represents the maximum width of the upper side flow channel. λ s This is the side channel width contraction coefficient. z This refers to the axial position.

6. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 1, characterized in that, The optimal channel widths of the first anisotropic spiral channel and the second anisotropic spiral channel are as follows: In the formula, w * Optimal minimum channel width ρ For cutting fluid density, ω This refers to the angular velocity of the grinding head.

7. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 1, characterized in that, The number of first anisotropic spiral flow channels and the number of second anisotropic spiral flow channels are determined according to the following formula: In the formula, N For the number of flow channels, D The diameter of the grinding head. σ b The bending strength of the grinding head material. K s For safety reasons, F t The grinding force experienced by a single abrasive grain. d g The average particle size of the abrasive grains. Q This refers to the volumetric flow rate of the grinding fluid. v 液 The average flow velocity of the grinding fluid in the flow channel. H For flow channel depth, w max The maximum width of the flow channel. w min This is the minimum width of the flow channel.

8. The anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in claim 1, characterized in that, The number of the first anisotropic spiral flow channels and the spiral grooves of the second anisotropic spiral flow channels satisfy the arc length relationship: In the formula, d s Let d be the infinitesimal arc length of the spiral curve. r It represents a small change in the radial direction. r For the current radius, d φ It is a tiny angular change.

9. A grinding apparatus, characterized in that, The invention includes an anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in any one of claims 1-8, and further includes an ultrasonic electric spindle and a micro-lubrication device, as well as a multi-degree-of-freedom rotating robotic arm; the ultrasonic electric spindle and the micro-lubrication device include an ultrasonic electric spindle, a nozzle, and an ultrasonic generator; wherein, the ultrasonic electric spindle is connected to the end of the multi-degree-of-freedom rotating robotic arm, the ultrasonic electric spindle is connected to the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head, the ultrasonic generator controls the ultrasonic electric spindle, and a cutting fluid nozzle is provided on the side of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head.

10. The fabrication process of the anisotropic spiral flow channel gradient traction self-contained cylindrical grinding head as described in any one of claims 1-8, characterized in that, as follows: Preparation of matrix; An anisotropic spiral flow channel is formed on the end face of the substrate by photolithography-electrochemical etching, and a first anisotropic spiral flow channel and a second anisotropic spiral flow channel are formed on the side face of the substrate. A spiral turning transition flow channel is set at the junction of the side face and the end face of the substrate. The first anisotropic spiral flow channel, the second anisotropic spiral flow channel, and the spiral turning transition flow channel are treated to form a hydrophilic surface; Electroplated insulating varnish is applied to the grooves of the first anisotropic spiral flow channel, the second anisotropic spiral flow channel, and the spiral turning transition flow channel. Sand is applied to the end face and sides of the substrate to fix the abrasive on the end face of the substrate; Peel off the electroplated insulating varnish; The sides and end faces of the grinding head are subjected to composite electroplating to form a nickel substrate; A hydrophobic layer is formed on the nickel surface through surface chemical modification; The abrasive grains are treated to form a hydrophilic structure at one end.

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