An inner cyclone knife block

Abstract

The utility model discloses an inner cyclone tool holder, which comprises the following components: a machine tool end assembly comprises a first base, a speed increasing gear set, a power shaft and an input transmission gear, the speed increasing gear set comprises an input gear and a first speed increasing gear in meshing, and a second speed increasing gear and a third speed increasing gear in meshing, the input gear and the third speed increasing gear are located on the same side of the first speed increasing gear; a rotary tool end assembly comprises a second base, a speed reducing gear set, a driving cylinder and an output transmission gear, the speed reducing gear set comprises an output gear and a first speed reducing gear in meshing, and a second speed reducing gear and a third speed reducing gear in meshing, the output transmission gear and the third speed reducing gear are coaxially fixed and located on the same side of the second speed reducing gear, the input transmission gear is in meshing with the output transmission gear, and the driving cylinder is provided with a tool particle ring seat. The utility model has high space utilization, compact structure, high milling precision, improved load capacity, low failure rate and long service life.

Description

Technical Field

[0001] This utility model relates to the field of cutting tool accessories, and in particular to an internal vortex cutting tool holder. Background Technology

[0002] In industrial applications, a tool holder is a mechanical component used for the precise installation, positioning, and clamping of cutting tools. It is a key component connecting the machine tool spindle or tool holder to the cutting tool. A cyclone milling machine is a high-speed thread milling device used with ordinary machine tools. It uses carbide forming cutters on a high-speed rotating disc to perform thread machining on the workpiece.

[0003] Internal cyclone cutter holders are used to achieve internal cyclone milling, which features a long envelope stroke and large cutting depth, effectively adapting to the machining of high-precision threads. In related technologies, internal cyclone cutter holders include a rotating body for connecting the cutting inserts. This rotating body is connected to the machine tool spindle or other power mechanism, driving the rotating body and its mounted cutting inserts to rotate and complete the milling process. However, this structure has weak milling load-bearing capacity and is prone to vibration and misalignment during milling, resulting in insufficient milling accuracy. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes an internal vortex tool holder, which has a compact and reliable structure, effectively improving the reliability and machining accuracy of milling operations, and possessing strong load-bearing capacity.

[0005] An internal cyclone blade holder according to an embodiment of the present utility model includes: The machine tool end assembly includes a first base, a speed-increasing gear set, and a power shaft and an input transmission gear rotatably connected to the first base. The speed-increasing gear set includes an input gear and a first speed-increasing gear meshing together, and a second speed-increasing gear and a third speed-increasing gear meshing together. The first speed-increasing gear and the second speed-increasing gear are coaxially fixed. The power shaft is coaxially fixed to the input gear. The input transmission gear is coaxially fixed to the third speed-increasing gear. The input gear and the third speed-increasing gear are both located on the same side of the first speed-increasing gear. The rotary cutter end assembly includes a second base, a reduction gear set, and a drive cylinder and an output transmission gear rotatably connected to the second base. The reduction gear set includes an output gear and a first reduction gear meshing with each other, as well as a second reduction gear and a third reduction gear meshing with each other. The first reduction gear and the second reduction gear are coaxially fixed. The drive cylinder is coaxially fixed to the output gear. The output transmission gear and the third reduction gear are coaxially fixed and both located on the same side of the second reduction gear. The second base is connected to the first base. The input transmission gear and the output transmission gear are meshed with each other. One end of the drive cylinder is provided with a cutter head ring seat.

[0006] In this embodiment, the drive cylinder is perpendicular to the power shaft, and the input and output transmission gears are perpendicular to each other. Both the input and output transmission gears are bevel gears.

[0007] In this embodiment, the ratio of the transmission ratio of the speed-increasing gear set to the transmission ratio of the speed-reducing gear set is 1, and the transmission ratio of the input transmission gear to the output transmission gear is 1.

[0008] In this embodiment, the transmission ratio of the speed-increasing gear set is 2:3, and the transmission ratio of the speed-reducing gear set is 3:2.

[0009] In this embodiment, the first base is provided with a circular rotating insertion hole, the second base is provided with a cylindrical positioning boss, one side of the rotating insertion hole is provided with an adjusting screw hole, the positioning boss passes through the rotating insertion hole, and an adjusting screw is threadedly connected in the adjusting screw hole. The adjusting screw is used to abut against and lock the positioning boss.

[0010] In this embodiment, a first base is connected to a first cover plate, and the speed-increasing gear set, the power shaft, and the input transmission gear are all disposed between the first base and the first cover plate. A second base is connected to a second cover plate, and the speed-reducing gear set, the drive cylinder, and the output transmission gear are all disposed between the second base and the second cover plate.

[0011] In this embodiment, the surface of the first base is provided with a helix angle mark, and the second cover plate is provided with a pointer mark adjacent to the helix angle mark.

[0012] In this embodiment, the blade ring seat is provided with multiple blade mounting grooves distributed along a circumferential trajectory.

[0013] In this embodiment, a power gear is provided at the end of the power shaft away from the input gear.

[0014] The embodiments of this utility model have at least the following beneficial effects: By using a parallel arrangement of speed-increasing and speed-reducing gear sets, the overall structure's dimensions in a single dimension can be effectively controlled, resulting in high space utilization and a compact, small overall structure. Furthermore, the concentrated mass distribution of the internal cyclone cutter holder effectively improves its dynamic balance and operational stability during high-speed rotation, providing high stability and reliability for internal cyclone milling and significantly enhancing milling accuracy. The speed-reducing gear set transmits the torsional force input from the output transmission gear to the drive cylinder in a speed-reducing and torque-increasing manner, significantly improving the drive cylinder's output torque and load-bearing capacity, effectively ensuring the cutter can operate under high-load milling conditions. It can generate a continuous, stable and reliable milling force, resulting in high reliability and machining quality in milling. By optimizing the force transmission path through the reduction gear set, most of the reaction force generated during the operation of the drive cylinder is directly applied to the second base through the reduction gear set. The impact and vibration forces can be effectively dispersed to various areas of the tool holder and absorbed and buffered, which can effectively avoid the local concentration of torque stress, effectively improve the operational stability of the overall structure, and result in a low failure rate and long service life. In addition, an effective and reliable physical isolation is formed between the machine tool end assembly and the rotary cutter end assembly, which can effectively reduce the operating burden of the power shaft and further reduce the failure rate. Attached Figure Description

[0015] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which: Figure 1 This is a three-dimensional structural diagram of the inner cyclone blade holder according to an embodiment of the present utility model; Figure 2 This is a three-dimensional structural diagram of the inner cyclone blade holder from another perspective, according to an embodiment of the present utility model. Figure 3 This is a top view of the internal cyclone blade holder according to an embodiment of the present utility model; Figure 4 For along Figure 3 A schematic diagram of the cross-sectional structure of line A-A'; Figure 5 This is an exploded structural diagram of the inner cyclone blade holder according to an embodiment of the present utility model.

[0016] Figure label: Machine tool end assembly 100, first base 110, rotary socket 111, adjusting screw hole 112, adjusting screw 113, helix angle mark 114, input gear 121, first speed-increasing gear 122, second speed-increasing gear 123, third speed-increasing gear 124, power shaft 130, power gear 131, input transmission gear 140, first cover plate 150; The rotary cutter end assembly 200, the second base 210, the positioning boss 211, the output gear 221, the first reduction gear 222, the second reduction gear 223, the third reduction gear 224, the drive cylinder 230, the output transmission gear 240, the cutting edge ring seat 250, the cutting edge mounting groove 251, the second cover plate 260, and the pointer mark 261. Detailed Implementation

[0017] The embodiments of this utility model are described in detail below. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0018] In the description of this utility model, it should be understood that the orientation descriptions, such as up, down, left, right, front, and back, are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0019] In the description of this utility model, if the wire sleeve or frame is mentioned, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features or the order of the technical features.

[0020] In the description of this utility model, unless otherwise explicitly defined, terms such as "setting," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0021] In industrial applications, a tool holder is a mechanical component used for the precise installation, positioning, and clamping of cutting tools. It is a key component connecting the machine tool spindle or tool holder to the cutting tool. A whirl milling machine is a high-speed thread milling device used with ordinary machine tools. It uses carbide forming cutters on a high-speed rotating disc to perform thread machining on the workpiece. An internal whirl milling tool holder is used to achieve internal whirl milling, which features a long envelope stroke and large cutting depth, effectively adapting to the machining of high-precision threads.

[0022] In internal cyclone milling, the internal cyclone cutter holder is connected to the milling power structure, thereby driving the cutting inserts in the internal cyclone cutter holder to rotate to achieve milling. In related technologies, the internal cyclone cutter holder has a rotating body for connecting the cutting inserts. The rotating body is connected to the machine tool spindle or other power mechanism through a transmission component, thereby driving the rotating body and the cutting inserts mounted thereon to rotate to complete the milling process. However, this structure has a weak milling load-bearing capacity and is prone to vibration and displacement during the milling process, resulting in insufficient milling accuracy. Moreover, the impact and vibration generated by this structure during the milling process can easily damage the transmission components and even damage the expensive machine tool spindle, severely shortening the service life of the equipment.

[0023] The following is for reference only. Figure 1 To be continued Figure 5 The internal cyclone tool holder described in this utility model embodiment has a compact and reliable structure, which can effectively improve the reliability and machining accuracy of milling operations and has a strong load-bearing capacity.

[0024] Reference Figures 1 to 5 An embodiment of the present invention provides an internal cyclone blade holder, comprising: The machine tool end assembly 100 includes a first base 110, a speed-increasing gear set, and a power shaft 130 and an input transmission gear 140, both rotatably connected to the first base 110. The input transmission gear 140 is connected to the power shaft 130 via the speed-increasing gear set. The speed-increasing gear set includes an input gear 121 and a first speed-increasing gear 122 meshing together, and a second speed-increasing gear 123 and a third speed-increasing gear 124 meshing together. The input gear 121, the first speed-increasing gear 122, the second speed-increasing gear 123, and the third speed-increasing gear 124 are all rotatably connected to the first base 110. The first speed-increasing gear 122 and the second speed-increasing gear 123 are coaxially fixedly connected, and the input gear 121 and the third speed-increasing gear 124 are coaxial, that is, the axis of the input gear 121 and the axis of the third speed-increasing gear 124 are coaxial. The axes of gears 124 are collinear. The power shaft 130 is coaxially fixedly connected to the input gear 121. The input transmission gear 140 is coaxially fixedly connected to the third speed-increasing gear 124. The input gear 121 and the third speed-increasing gear 124 are both located side by side on the same side of the first speed-increasing gear 122 and the second speed-increasing gear 123. The first speed-increasing gear 122 and the second speed-increasing gear 123 form a speed-increasing bypass gear string. The input gear 121 and the third speed-increasing gear 124 form a speed-increasing main gear string. The speed-increasing bypass gear string is located on one side of the speed-increasing main gear string. This can effectively control the dimensions in a single dimension, thereby improving the compactness of the overall structure of the internal cyclone cutter holder. It can fully improve the utilization rate of three-dimensional space, concentrate the mass distribution, and stabilize the operation. The power shaft 130 is used to connect the spindle of the machine tool. The rotary cutter end assembly 200 includes a second base 210, a reduction gear set, and a drive cylinder 230 and an output transmission gear 240, all rotatably connected to the second base 210. The reduction gear set includes an output gear 221 and a first reduction gear 222 meshing together, and a second reduction gear 223 and a third reduction gear 224 meshing together. The output gear 221, the first reduction gear 222, the second reduction gear 223, and the third reduction gear 224 are all rotatably connected to the second base 210. The first reduction gear 222 and the second reduction gear 223 are coaxially fixedly connected. The output gear 221 and the third reduction gear 224 are rotatably connected to the second base 210. 4. Coaxiality: The axis of the output gear 221 is collinear with the axis of the third reduction gear 224. The drive cylinder 230 is coaxially fixedly connected to the output gear 221. The output transmission gear 240 and the third reduction gear 224 are coaxially fixedly connected, and both are located side-by-side on the same side of the first reduction gear 222 and the second reduction gear 223. The first reduction gear 222 and the second reduction gear 223 form a reduction bypass gear train, and the output transmission gear 240 and the third reduction gear 224 form a reduction main gear train. The reduction bypass gear train is located on one side of the reduction main gear train, enabling… Effective control of single-dimensional dimensions improves the overall compactness of the internal cyclone cutter holder structure, maximizing three-dimensional space utilization, concentrating mass distribution, and ensuring stable operation. The second base 210 connects to the first base 110, and the input transmission gear 140 meshes with the output transmission gear 240. One end of the drive cylinder 230 is equipped with a cutting disc ring seat 250. The drive cylinder 230 is connected to the output transmission gear 240 via a reduction gear set. The reduction gear set reduces the torque of the output transmission gear 240 to rotate the drive cylinder 230, effectively improving the load-bearing capacity of the drive cylinder 230 and ensuring stable and reliable milling force. This design effectively improves the reliability of milling operations. Most of the reaction force generated by the drive cylinder 230 during operation is applied to the second base 210 through the reduction gear set. In addition, the gear set between the machine tool end and the rotary cutter end can form an effective physical isolation. The impact and vibration forces generated by the cutter ring seat 250 during operation are effectively dispersed to various areas of the cutter seat to achieve absorption and buffering. This not only effectively avoids torque stress concentration but also effectively reduces the operating burden of the power shaft 130. It can also prevent direct damage to the machine tool spindle due to overload or other faults, effectively improve the structural accuracy of the applied device, and effectively extend its service life.

[0025] By arranging the speed-increasing and speed-reducing gear sets in parallel, the various gear sets can be distributed in three-dimensional space within the tool holder. This effectively controls the overall structural dimensions in a single dimension, avoiding the impact of excessive size in any single dimension on installation and use. It boasts high space utilization, a compact and small overall structure, and concentrated mass distribution within the internal cyclone tool holder. This effectively improves the dynamic balance and operational stability of the tool holder during high-speed rotation, ensuring structural stability and anti-deviation performance during milling. It offers high stability and reliability for internal cyclone milling, effectively improving milling accuracy. The speed-reducing gear set transmits the torsional force input from the output transmission gear 240 to the drive cylinder 230 in a speed-reducing and torque-increasing manner, significantly improving the output torque and load-bearing capacity of the drive cylinder 230. This effectively ensures that the cutting tool can generate continuous, stable, and reliable milling force even under high-load milling conditions, thereby improving the reliability and quality of milling operations. By optimizing the force transmission path, most of the reaction force generated by the drive cylinder 230 during operation is directly applied to the second base 210 through the reduction gear set. The impact and vibration forces generated by the cutter ring seat 250 during operation can be effectively dispersed to various areas of the cutter holder and absorbed and buffered. This effectively avoids the local concentration of torque stress, which can effectively improve the overall structural stability and reduce the failure rate, resulting in a longer service life. In addition, the machine tool end and the rotary cutter end are connected by the meshing of the input transmission gear 140 and the output transmission gear 240, which can form an effective and reliable physical isolation. Combined with the above-mentioned force transmission mechanism, it can effectively reduce the operating burden of the power shaft 130, avoid direct damage to the machine tool spindle due to overload and other faults, further reduce the failure rate, and effectively protect the power equipment connected to the power shaft 130. This not only protects the valuable main machine tool equipment, but also significantly improves the accuracy retention and service life of the applied structure due to the improvement of the overall stress condition.

[0026] It is understandable that the drive cylinder 230 is perpendicular to the power shaft 130, and the input transmission gear 140 and output transmission gear 240 are perpendicular to each other. Both the input transmission gear 140 and the output transmission gear 240 are bevel gears. By using bevel gears as the input transmission gear 140 and the output transmission gear 240, the power is redirected 90 degrees from the axis parallel to the power shaft 130 to the axis parallel to the drive cylinder 230. This effectively optimizes the spatial layout of the tool holder, making the overall shape of the tool holder more adaptable to the spatial constraints of the machine tool's working cavity, and effectively improving space utilization.

[0027] Specifically, the drive cylinder 230 is located on the side of the first reduction gear 222 opposite to the speed-increasing gear set, providing ample clearance for the drive cylinder 230 and the insert ring seat 250 to pass through. When applied to machine tool machining, the path of the workpiece being picked up, placed, and translated in the insert ring seat 250 is perpendicular to the machine tool spindle, which improves adaptability to the environmental space and can further reduce the size requirements in a single dimension, providing a larger stroke space for machining large workpieces.

[0028] It is understandable that the ratio of the transmission ratio of the speed-increasing gear set to that of the speed-reducing gear set is 1:1, and the transmission ratio between the input transmission gear 140 and the output transmission gear 240 is also 1:1. Therefore, the overall transmission ratio of the entire transmission system is 1:1, and the speed input to the machine tool spindle via the power shaft 130 is consistent with the final speed of the cutting tool ring holder 250. The speed of the cutting tool ring holder 250 can be directly controlled via the machine tool spindle through the power shaft 130. The control system does not require complex speed conversion, resulting in direct and reliable control, and extremely convenient adjustment. This simplifies the CNC programming and operation process of the machine tool, making application design convenient.

[0029] Understandably, the speed-increasing gear set has a transmission ratio of 2:3, and the speed-reducing gear set has a transmission ratio of 3:2. By controlling the speed change rate to within 1, the stability and reliability of the overall structure's operation can be further improved. Choosing a speed increase ratio less than 1 and a transmission ratio greater than 1, and controlling the speed change rate of each stage within a reasonable range, avoids excessive single-stage speed changes, smooths the power transmission process, and reduces gear meshing impact and noise. This balanced speed change design helps to further improve the stability and reliability of the overall structure's operation, while ensuring a significant gain in the final output torque.

[0030] Understandably, the first base 110 is provided with a circular rotating insertion hole 111, and the second base 210 is provided with a cylindrical positioning boss 211. An adjusting screw hole 112 is provided on one side of the rotating insertion hole 111. The positioning boss 211 passes through the rotating insertion hole 111 so that the first base 110 and the second base 210 can rotate around the axis of the positioning boss 211. An adjusting screw 113 is threaded into the adjusting screw hole 112. The adjusting screw 113 is used to engage with the adjusting screw hole 112 to abut against and lock the positioning boss 211, thereby locking the positions of the first base 110 and the second base 210.

[0031] The above structure constitutes an adjustable angle positioning mechanism. The cooperation between the positioning boss 211 and the rotating insertion hole 111 ensures the coaxiality of the two bases, while allowing the second base 210 to rotate relative to the first base 110. By tightening the adjusting screw 113 to abut against the positioning boss 211, the relative angular position of the two components can be conveniently and reliably locked. This internal cyclone cutter holder can flexibly adjust the milling helix angle phase of the insert ring seat 250 according to processing requirements, which can effectively improve processing adaptability and flexibility.

[0032] It is understood that the first base 110 is connected to the first cover plate 150, and the speed-increasing gear set, power shaft 130, and input transmission gear 140 are all located between the first base 110 and the first cover plate 150. The second base 210 is connected to the second cover plate 260, and the speed-reducing gear set, drive cylinder 230, and output transmission gear 240 are all located between the second base 210 and the second cover plate 260. The connections between the various structures in the tool holder can be achieved through conventional structures such as bearings, screws, nuts, oil seals, washers, and retaining rings, which will not be elaborated here. The first cover plate 150 and the first base 110 together form a closed housing to house and protect all transmission components at the machine tool end; similarly, the second cover plate 260 and the second base 210 form the transmission housing at the rotary cutter end. This allows for convenient disassembly, lubrication, and maintenance of the tool holder. When maintenance or gear replacement is required, only the corresponding cover plate needs to be opened for direct operation, resulting in high assembly and maintenance efficiency and reducing the long-term use and maintenance costs of the equipment.

[0033] It is understood that the surface of the first base 110 is provided with a helix angle mark 114, and the second cover plate 260 is provided with a pointer mark 261 adjacent to the helix angle mark 114. The pointer mark 261 is used to indicate the helix angle in conjunction with the helix angle mark 114.

[0034] The helix angle mark 114 and the pointer mark 261 together form a simple yet effective angle scale, adding a precise angle indication function to the adjustable angle mechanism. Operators can intuitively and accurately read and set the helix angle or phase angle of the insert ring 250, ensuring accuracy and repeatability when adjusting the tool angle, and effectively realizing high-precision milling operations that require precise control of the tool helix angle.

[0035] Understandably, the insert ring seat 250 is provided with multiple insert mounting slots 251 distributed along a circumferential trajectory. Each insert mounting slot 251 is equipped with a milling cutter insert, and the cutting edge of each milling cutter insert faces the center of the insert ring seat 250, thereby performing cyclone milling on the workpiece.

[0036] The multi-particle evenly distributed design achieves a balance of cutting forces, improving the stability of the milling process; all milling cutter edges face the center, ensuring efficient whirl milling of the workpiece's inner hole surface. The detachable installation method facilitates the replacement and indexing of individual cutters, and there is no need to replace the entire cutter ring 250 after wear, resulting in good economy and convenient maintenance.

[0037] Understandably, the end of the power shaft 130 away from the input gear 121 is provided with a power gear 131, which is used to connect to an external power source.

[0038] The power gear 131 can also be configured with standard mechanical connection structures such as splines and couplings, which can effectively enhance the versatility and compatibility of the tool holder with different machine tool spindles. Through modular interface design, this internal cyclone tool holder can be quickly and reliably installed as a standard accessory onto various machine tools with corresponding output functions, making it widely applicable.

[0039] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An internal cyclone blade holder, characterized in that, include: The machine tool end assembly (100) includes a first base (110), a speed-increasing gear set, and a power shaft (130) and an input transmission gear (140) rotatably connected to the first base (110). The speed-increasing gear set includes an input gear (121) and a first speed-increasing gear (122) meshing with each other, and a second speed-increasing gear (123) and a third speed-increasing gear (124) meshing with each other. The first speed-increasing gear (122) and the second speed-increasing gear (123) are coaxially fixed. The power shaft (130) is coaxially fixed to the input gear (121), and the input transmission gear (140) is coaxially fixed to the third speed-increasing gear (124). The input gear (121) and the third speed-increasing gear (124) are both located on the same side of the first speed-increasing gear (122). The rotary cutter end assembly (200) includes a second base (210), a reduction gear set, and a drive cylinder (230) and an output transmission gear (240) rotatably connected to the second base (210). The reduction gear set includes an output gear (221) and a first reduction gear (222) meshing with each other, and a second reduction gear (223) and a third reduction gear (224) meshing with each other. The first reduction gear (222) is coaxially fixed with the second reduction gear (223). The drive cylinder (230) is coaxially fixed with the output gear (221). The output transmission gear (240) and the third reduction gear (224) are coaxially fixed and are both located on the same side of the second reduction gear (223). The second base (210) is connected to the first base (110). The input transmission gear (140) meshes with the output transmission gear (240). One end of the drive cylinder (230) is provided with a cutter ring seat (250).

2. The internal cyclone blade holder according to claim 1, characterized in that, The drive cylinder (230) is perpendicular to the power shaft (130). The input transmission gear (140) and the output transmission gear (240) are perpendicular to each other. Both the input transmission gear (140) and the output transmission gear (240) are bevel gears.

3. The internal cyclone blade holder according to claim 1, characterized in that, The ratio of the transmission ratio of the speed-increasing gear set to the transmission ratio of the speed-reducing gear set is 1, and the transmission ratio of the input transmission gear (140) to the output transmission gear (240) is 1.

4. The internal cyclone blade holder according to claim 3, characterized in that, The transmission ratio of the speed-increasing gear set is 2:3, and the transmission ratio of the speed-reducing gear set is 3:

2.

5. The internal cyclone blade holder according to claim 1, characterized in that, The first base (110) is provided with a circular rotating insertion hole (111), and the second base (210) is provided with a cylindrical positioning boss (211). An adjusting screw hole (112) is provided on one side of the rotating insertion hole (111). The positioning boss (211) passes through the rotating insertion hole (111), and an adjusting screw (113) is threaded into the adjusting screw hole (112). The adjusting screw (113) is used to abut and lock the positioning boss (211).

6. The internal cyclone blade holder according to claim 5, characterized in that, The first base (110) is connected to a first cover plate (150). The speed-increasing gear set, the power shaft (130) and the input transmission gear (140) are all disposed between the first base (110) and the first cover plate (150). The second base (210) is connected to a second cover plate (260). The speed-reducing gear set, the drive cylinder (230) and the output transmission gear (240) are all disposed between the second base (210) and the second cover plate (260).

7. The internal cyclone blade holder according to claim 6, characterized in that, The surface of the first base (110) is provided with a helical angle mark (114), and the second cover plate (260) is provided with a pointer mark (261) adjacent to the helical angle mark (114).

8. The internal cyclone blade holder according to claim 1, characterized in that, The blade ring seat (250) is provided with multiple blade mounting grooves (251) distributed along a circumferential trajectory.

9. The internal cyclone blade holder according to claim 1, characterized in that, The power shaft (130) has a power gear (131) at one end away from the input gear (121).

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