A tool holder assembly of a numerical control high-efficiency gear hobbing machine

Abstract

This invention relates to the field of CNC machine tool technology and discloses a tool post assembly for a high-efficiency CNC gear hobbing machine, including a tool post base. A top transmission assembly is rotatably connected to the inner cavity of the tool post base. A bottom mounting block is fixedly mounted on one side of the bottom of the tool post base, and a sliding assembly is slidably sleeved on the other side of the bottom of the tool post base. An adjusting screw for driving the sliding assembly is rotatably connected to the side of the tool post base near the sliding assembly. When the machine tool cutting causes radial runout of the hob, the minute displacement generated by the runout reverses and compresses the rigid wedge and the sealed hydraulic oil, converting the originally difficult-to-handle solid mechanical vibration energy into hydraulic oil pressure pulsations. These pressure pulsations are guided to different dissipation paths according to their frequency characteristics. Through a spiral inertial microtube, utilizing the mass amplification effect of the slender tube on the fluid, a reverse inertial force with a phase lag of 180° is generated, mechanically canceling and reducing the low-frequency amplitude.

Description

Technical Field

[0001] This invention relates to the field of CNC machine tool technology, specifically to a tool post assembly for a high-efficiency CNC gear hobbing machine. Background Technology

[0002] CNC gear hobbing machines are key equipment in gear machining, and their machining accuracy and efficiency directly affect the manufacturing quality of gears. The tool post assembly, as the core component of the gear hobbing machine, is responsible for mounting and driving the hob for cutting. In existing technologies, the hob is typically fixed to the tool post spindle via a mechanical clamping structure (such as a flange, bolts, or chuck). While this rigid clamping method is simple in structure, it has significant shortcomings in high-speed, heavy-load cutting processes: the hob generates radial runout under cutting forces, which includes a complex vibration spectrum from low to high frequencies. Traditional rigid mechanical clamping structures lack effective active vibration reduction and damping mechanisms for this type of vibration, especially high-frequency chatter with small amplitudes. Vibration is directly transmitted to the tool post and the machine tool body, exacerbating tool wear and affecting machining accuracy and surface finish; furthermore, continuous vibration impact can shorten the service life of critical components such as the tool post bearings, and in severe cases, may even lead to safety accidents such as chipping. Therefore, how to effectively suppress the radial vibration of the hob during the cutting process, especially to achieve wideband dynamic damping from low frequency to high frequency, has become a key challenge in improving the machining performance and reliability of CNC gear hobbing machines. Summary of the Invention

[0003] This invention provides a tool holder assembly for a CNC high-efficiency gear hobbing machine, which solves the problems mentioned in the background art.

[0004] The present invention provides the following technical solution: a tool holder assembly for a CNC high-efficiency gear hobbing machine, comprising a tool holder base, wherein a top transmission assembly is rotatably connected to the inner cavity of the tool holder base; A bottom mounting block is fixedly mounted on one side of the bottom of the tool holder base, and a sliding sleeve is slidably fitted on the other side of the bottom of the tool holder base. The tool holder base is rotatably connected to an adjusting screw for driving the sliding assembly to move on the side closest to the sliding assembly. The sliding assembly is threadedly connected to the adjusting screw. The bottom assembly block is fixedly fitted with a fixed support head, and a hobbing cutter is fitted between the fixed support head and the sliding kit.

[0005] As a preferred embodiment of the present invention, the top transmission assembly includes a power input gear, the bottom of which is engaged with meshing teeth, and a mounting shaft is fixedly mounted on the side of the meshing teeth near the adjusting screw, and a power transmission spline is fitted onto the outer wall of the mounting shaft.

[0006] As a preferred embodiment of the present invention, the sliding kit includes a movable housing, and a clamping spindle is rotatably connected inside the movable housing.

[0007] As a preferred embodiment of the present invention, the clamping spindle has a sealed annular hydraulic cavity inside, and the annular hydraulic cavity is filled with hydraulic oil. The clamping spindle is also provided with parallel spiral inertial microtubes and high-frequency overflow channels, and both the spiral inertial microtubes and the high-frequency overflow channels are connected to the annular hydraulic cavity. A disc spring valve is installed in the high-frequency overflow channel; When the clamping spindle is subjected to radial excitation force and generates relative displacement, the hydraulic oil in the annular hydraulic chamber is pressurized and selectively flows through the spiral inertial microtube or the high-frequency overflow channel.

[0008] As a preferred embodiment of the present invention, the disc spring valve is configured as a mechanical friction valve, and the opening pressure threshold of the disc spring valve is matched with the pressure generated by the hydraulic oil when the clamping spindle experiences high-frequency chatter, so as to open the high-frequency overflow channel under high-frequency and high-pressure conditions.

[0009] As a preferred embodiment of the present invention, the fixed support head is rotatably connected to a center sleeve, one end of the hobbing cutter is engaged and driven by the clamping spindle, and the other end of the hobbing cutter is rotatably inserted into the center sleeve.

[0010] As a preferred embodiment of the present invention, the outer wall of the clamping spindle is provided with an oil injection hole, the oil injection hole is connected to the annular hydraulic cavity, and the internal thread of the oil injection hole is sealed with a sealing plug. The annular hydraulic chamber is also fixedly equipped with an elastic compensating element for compensating for the thermal expansion and contraction of hydraulic oil.

[0011] The present invention has the following beneficial effects: The tool holder assembly of this CNC high-efficiency gear hobbing machine solves the problem that rigid clamping cannot effectively suppress radial vibration by changing the clamping force source of the hob parts from a purely mechanical structure to a clamping method of hydraulic oil hydrostatic driving rigid wedges, and using the hydraulic oil used for clamping as a medium for dynamic vibration reduction.

[0012] Its basic principle is as follows: during initial clamping, the external hydraulic pump source injects high-pressure hydraulic oil into the annular hydraulic chamber of the clamping spindle. The hydraulic oil pressure is transmitted to the sealed mounting cavity through Pascal's law, driving the rigid wedge to contract and rigidly lock the rhomboid end face of the hob, forming a stable initial clamping. When machine tool cutting causes radial runout of the hob, the tiny displacement generated by the runout compresses the rigid wedge and the sealed hydraulic oil in the opposite direction, converting the originally difficult-to-handle solid mechanical vibration energy into hydraulic oil pressure pulsation. This pressure pulsation is guided to different dissipation paths according to its frequency characteristics. For low-frequency pressure pulsation, it generates a reverse inertial force with a phase lag of 180° through the spiral inertial microtube, which is opposite to the direction of the current excitation force of the tool. This force is mechanically canceled to reduce the low-frequency amplitude. For high-frequency pressure pulsation, the spiral inertial microtube will experience fluid lock-up due to its inductive reactance characteristics, forcing the high-pressure oil to open the disc spring valve in the parallel high-frequency overflow channel. The mechanical kinetic energy of the high-frequency vibration is forcibly converted into heat energy dissipation through the metal dry friction between the disc spring valve plates. Meanwhile, the elastic buffer chamber and elastic dividing membrane can store energy and press the hydraulic oil back when the hob rebounds under force, ensuring that the rigid wedge does not slip and maintaining the clamping force. Attached Figure Description

[0013] Figure 1 This is a three-dimensional structural diagram of the present invention; Figure 2 This is a schematic diagram of the bottom assembly block structure of the present invention; Figure 3 This is a schematic diagram of the top transmission assembly structure of the present invention; Figure 4 This is a schematic diagram of the adjusting screw structure of the present invention; Figure 5 This is a schematic diagram of the hobbing cutter structure of the present invention; Figure 6 This is a schematic diagram of the mounting structure for clamping the spindle and the hobbing cutter of the present invention; Figure 7 This is a schematic diagram of the cross-sectional structure of the clamping spindle of the present invention; Figure 8 This is a schematic diagram of the clamping spindle structure of the present invention.

[0014] In the diagram: 1. Tool holder base; 2. Top transmission assembly; 3. Bottom assembly block; 4. Sliding kit; 5. Fixed support head; 6. Hobbing cutter; 7. Adjusting screw; 201. Power input gear; 202. Meshing gear; 203. Mounting shaft; 204. Power transmission spline; 401. Moving housing; 402. Rotating inner wheel; 403. Bearing ring; 404. Clamping spindle; 4041, Spindle body; 4042, End slot; 4043, Sealed mounting cavity; 4044, Rigid wedge; 4045, Annular hydraulic chamber; 4046, High-frequency overflow channel; 4047, Helical inertial microtube; 4048, Internal guide post; 4049, Piston spring; 40410, Relief piston; 40411, Disc spring valve; 40412, Oil drain hole; 40413, Buffer chamber; 40414, Elastic dividing membrane; 601. Outer layer of the hob; 602. Internal fixing core; 603. Abutment groove. Detailed Implementation

[0015] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0016] It should be noted that, in the embodiments of this application, "fixed assembly" refers to a relatively fixed connection between two components achieved through conventional fasteners (such as bolts and screws), welding, riveting, or interference fits. "Rotary connection" refers to a connection between two components that can rotate relative to each other around an axis, typically achieved through slewing bearings, bushings, or other slewing support components. "Limited sleeve connection" refers to a connection where one component is fitted onto the outer wall of another component, forming a non-completely fixed displacement constraint in the axial and / or circumferential directions, allowing relative displacement in a specific direction (usually axial) while transmitting torque. "Fluid lock-in" refers to the phenomenon where, under specific flow conditions (such as high-frequency pulses), the effective impedance of the fluid in a pipeline tends to infinity due to inertial effects, thus impeding flow. "Mass amplification effect" refers to the phenomenon in slender pipelines where, because the cross-sectional area is much smaller than the length, the equivalent dynamic mass of the fluid is amplified, generating significant inertial forces.

[0017] Please see Figures 1-8 A tool holder assembly for a CNC high-efficiency gear hobbing machine includes a tool holder base 1, a top transmission assembly 2 rotatably connected to the inner cavity of the tool holder base 1, a bottom mounting block 3 fixedly mounted on one side of the bottom of the tool holder base 1, a sliding kit 4 slidably sleeved on the other side of the bottom of the tool holder base 1, and an adjusting screw 7 rotatably connected to the side of the tool holder base 1 near the sliding kit 4 for driving the sliding kit 4 to move. The bottom of the bottom assembly block 3 is fixedly equipped with a fixed support head 5, and a hobbing cutter 6 is fitted between the fixed support head 5 and the sliding kit 4.

[0018] In the above structure, according to the present invention, the tool holder assembly achieves quick assembly and disassembly of the hobbing cutter 6 by engaging one end of the hobbing cutter 6 with the fixed support head 5 and the other end with the sliding assembly 4, and driving the sliding assembly 4 along the bottom of the tool holder base 1 using the adjusting screw 7, thereby changing the distance between the sliding assembly 4 and the fixed support head 5. Simultaneously, the top transmission assembly 2 located inside the tool holder base 1 transmits external power to the sliding assembly 4, thereby driving the hobbing cutter 6 to rotate while it is clamped.

[0019] In practical applications, the overall working process of this CNC high-efficiency gear hobbing machine tool holder assembly is as follows: The operator drives the adjusting screw 7 to rotate, causing the sliding assembly 4 to move away from the fixed support head 5, thereby creating sufficient space between the two support points. One end of the hob cutter 6 is first inserted into the fixed support head 5, and then the adjusting screw 7 is driven in the opposite direction, causing the sliding assembly 4 to move towards the fixed support head 5 and insert into the other end of the hob cutter 6, completing pre-tightening and positioning. After the gear hobbing process begins, external power is connected to the top transmission group 2, and through the transmission path inside the sliding assembly 4, it ultimately drives the hob cutter 6 to rotate at high speed to cut the workpiece.

[0020] In a preferred embodiment: the top transmission assembly 2 includes a power input gear 201, the bottom of the power input gear 201 is engaged with a meshing gear 202, and a mounting shaft 203 is fixedly mounted on the side of the meshing gear 202 near the adjusting screw 7. A power transmission spline 204 is fitted onto the outer wall of the mounting shaft 203.

[0021] In the above structure, external power is connected to the power input gear 201, and the power input gear 201 transmits power to the mounting fixed shaft 203 and the power transmission spline 204 through meshing with the rotating gear 202. The power transmission spline 204 drives the hob 6 to rotate through the sliding kit 4, thereby realizing gear hobbing. When the power transmission spline 204 is limited and sleeved with the mounting fixed shaft 203, and the power transmission spline 204 moves and is adjusted by the sliding kit 4 through the adjusting screw 7, the mounting fixed shaft 203 and the power transmission spline 204 can maintain power transmission.

[0022] In a preferred embodiment: the sliding kit 4 includes a movable housing 401, an inner rotating wheel 402 inside the movable housing 401, a clamping spindle 404 fixedly mounted on the inner wall of the inner rotating wheel 402, and a bearing ring 403 fixedly mounted on the outer wall of the end of the clamping spindle 404. The clamping spindle 404 is rotatably connected to the movable housing 401 via the bearing ring 403, and the rotating inner wheel 402 meshes with the power transmission spline 204. The end of the power transmission spline 204 is rotatably connected to the top interior of the movable housing 401.

[0023] In the above structure, the power transmission spline 204 and the rotating inner wheel 402 are fixed by the movable housing 401, so that the power transmission spline 204 and the rotating inner wheel 402 are engaged. At the same time, the top two sides of the sliding kit 4 are slidably sleeved with the bottom of the tool holder base 1, so that the adjusting screw 7 can drive the sliding kit 4 to move along the bottom outer edge of the tool holder base 1.

[0024] In a preferred embodiment: the clamping spindle 404 includes a spindle body 4041, an end slot 4042 is provided at the end of the spindle body 4041 near the end of the hobbing cutter 6, a sealing mounting cavity 4043 is provided on the inner wall of the end slot 4042, a rigid wedge 4044 is fitted on the inner wall of the sealing mounting cavity 4043, an annular hydraulic cavity 4045 is provided at the bottom of the sealing mounting cavity 4043 near the adjusting screw 7, and a high-frequency overflow channel 4046 and a spiral inertial microtube 4047 are respectively provided inside the annular hydraulic cavity 4045 near the adjusting screw 7. An internal guide post 4048 is fixedly installed on the inner wall of the high-frequency overflow channel 4046. A piston spring 4049 is sleeved on the outer edge of the internal guide post 4048. The end of the piston spring 4049 abuts against a retracting piston 40410. A disc spring valve 40411 is sleeved on the outer wall of the internal guide column 4048 away from the piston spring 4049. An oil drain hole 40412 is opened on the inner wall of the high-frequency overflow channel 4046 located at the disc spring valve 40411. A buffer chamber 40413 is provided at the end of the high-frequency overflow channel 4046 near the adjusting screw 7, and an elastic dividing membrane 40414 is provided inside the buffer chamber 40413.

[0025] The clamping spindle 404 is also provided with an oil filling port for adding hydraulic oil near the annular hydraulic chamber 4045; An external hydraulic pump source injects hydraulic oil into the annular hydraulic chamber 4045 inside the clamping spindle 404 and builds up pressure to 10MPa. Since the annular hydraulic chamber 4045 is connected to the sealed mounting chamber 4043, the hydraulic oil drives the rigid wedge 4044 to contract, which rigidly locks the rhomboid end face of the hob cutter 6. Subsequently, the one-way micro-control valve at the oil injection port locks up, forming a closed flow field; When the machine tool starts cutting, the tool generates a small radial runout. This vibration directly compresses the rigid wedge 4044 and the hydraulic oil in the reverse direction, converting the mechanical vibration signal into the pressure pulsation ΔP of the hydraulic oil. Radial runout is classified into low frequency and high frequency; Low-frequency response period, such as 0~50Hz: Low-frequency pressure pulsation enters the parallel spiral inertial microtube 4047 through the rigid wedge 4044, the sealed mounting cavity 4043, and the annular hydraulic cavity 4045, generating fluid oscillation; High frequency response period such as >500Hz: High frequency pressure pulse causes fluid lock-up in spiral inertial microtube 4047, and pressure spikes forcibly open the parallel high frequency overflow channel 4046; Hydraulic oil flowing through the high-frequency overflow channel 4046 and the spiral inertial microtube 4047 merges into the tail pressure stabilizing buffer chamber composed of the elastic dividing membrane 40414 and the buffer chamber 40413. When the hobbing cutter 6 is subjected to force and rebounds, it is pressed back to the sealing installation chamber 4043 along the original path to ensure that the rigid wedge 4044 does not fall out and maintain the clamping force.

[0026] Traditional mechanical rigid vibration damping is extremely difficult to handle high-frequency, small amplitude vibrations.

[0027] This application transforms uncontrollable solid mechanical vibration into controllable fluid pressure pulsation; Using incompressible hydraulic oil as a medium, according to Pascal's law and the volume continuity equation, even a radial runout deformation of only a few micrometers (μm) in the tool will cause a drastic pressure change ΔP within the closed annular hydraulic chamber 4045.

[0028] At this point, the hydraulic oil itself becomes the carrier for transmitting vibrational energy.

[0029] By utilizing the "mass amplification effect" of the fluid through a slender pipe, an antiphase inertial force is generated to forcibly counteract the main vibration.

[0030] When low-frequency resonance occurs, hydraulic oil flows into the spiral inertial microtube 4047; According to the fluid inertia formula If=ρL / S; Where ρ is the liquid density, L is the tube length, and S is the minimum cross-sectional area; In a pipe with an extremely small cross-sectional area S and an extremely long length L, the equivalent dynamic mass of a very small amount of liquid will be drastically amplified.

[0031] Due to the combined effect of the flow resistance and fluid inertia of the 4047 microtube spiral inertia, the flow displacement of the liquid column inside the tube will lag behind the vibration displacement of the main shaft by a phase difference of 180°.

[0032] The lag-flowing hydraulic oil acts like a giant tuned liquid damper (TLD), generating a reverse inertial force F=ma that is opposite to the direction of the current excitation force of the tool, thus reducing the low-frequency amplitude through "mechanical cancellation".

[0033] The physical circuit is broken by utilizing the "inductive reactance" of high-frequency fluid, forcing the fluid to open the mechanical friction valve disc spring valve 40411, and converting mechanical kinetic energy into heat energy.

[0034] According to the fluid dynamics law ΔP=ρLdvdt, the pressure drop of a fluid is proportional to the square of the acceleration frequency.

[0035] When high-frequency flutter occurs at >500Hz, the fluid acceleration increases sharply, and the "dynamic fluid reactance" inside the spiral inertial microtube 4047 instantly approaches infinity, resulting in fluid lock-in. High-frequency high-pressure oil cannot enter the spiral inertial microtube 4047 at all.

[0036] When the high-voltage spike has nowhere to go, it can only forcefully push open the yield piston 40410 of the parallel high-frequency overflow channel 4046.

[0037] The retracting piston 40410 moves backward, forcibly compressing the stacked disc spring valve 40411; When the conical metal disc of the 40411 disc spring valve is flattened, strong radial relative slippage occurs between the discs.

[0038] According to the first law of thermodynamics, energy is conserved. The mechanical kinetic energy of high-frequency vibration is forcibly converted into heat energy and dissipated through the dry metal friction between the disc spring valves 40411.

[0039] At the same time, as the retracting piston 40410 moves backward, the high-frequency overflow channel 4046 drains the oil through the oil drain hole 40412, thus preventing the oil from deteriorating due to heat. The buffer chamber 40413 is divided into a pressure-stabilizing buffer chamber and an elastic buffer chamber by an elastic dividing membrane 40414. After the elastic dividing membrane 40414 is squeezed by hydraulic oil, the pressure accumulated in its elastic buffer chamber and the elastic dividing membrane 40414 will push the hydraulic oil back along the original path and flow back to the annular hydraulic chamber 4045 through the high-frequency overflow channel 4046, the oil drain hole 40412 and the spiral inertial microtube 4047.

[0040] In a preferred embodiment, the hobbing cutter 6 includes a hobbing cutter outer layer 601, an inner fixing core 602 is fixedly sleeved inside the hobbing cutter outer layer 601, and an abutment groove 603 is provided at the end of the inner fixing core 602.

[0041] This structure achieves stable installation of the hob cutter 6 by positioning and abutting with the end slot 4042 of the clamping spindle 404 through the abutment groove 603 at the end of the internal fixing core 602, while its other end engages with the fixed support head 5. As a specific implementation, the internal fixing core 602 can be made of high-strength alloy steel and is integrally fixed to the outer layer 601 of the hob through a heat-shrink or key connection to withstand enormous cutting torque.

[0042] Furthermore, it should be noted that in some optional embodiments, the external hydraulic pump source can be provided by the machine tool's built-in hydraulic station and connected to the oil inlet at the tail of the rotating clamping spindle 404 via a rotary joint. Alternatively, the drive of the adjusting screw 7 can be a manual wrench or an automatic control scheme by a servo motor. In the preferred design of the dimensional parameters, the inner diameter of the helical inertial microtube 4047 can be selected from 1mm to 3mm, and the total unfolded length is several hundred times its inner diameter to obtain sufficient mass amplification effect; the preload of the disc spring valve 40411 can be calibrated by adjusting the locking nut on the internal guide post 4048 so that its high-frequency opening threshold matches a specific chatter frequency band. The mating angle between the working cone surface of the rigid wedge 4044 and the rhomboid end face of the hob 6 is designed based on the self-locking principle to ensure that it can still maintain basic positioning after the hydraulic pressure is released.

[0043] It should be noted that, in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus.

[0044] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended technical solutions and their equivalents.

Claims

1. A tool holder assembly for a CNC high-efficiency gear hobbing machine, comprising a tool holder base (1), characterized in that: The inner cavity of the tool holder base (1) is rotatably connected to the top transmission assembly (2). A bottom mounting block (3) is fixedly mounted on one side of the bottom of the tool holder base (1), and a sliding sleeve (4) is slidably sleeved on the other side of the bottom of the tool holder base (1). The tool holder base (1) is rotatably connected to an adjusting screw (7) for driving the sliding kit (4) to move on the side near the sliding kit (4). The sliding assembly (4) is threadedly connected to the adjusting screw (7); The bottom assembly block (3) is fixedly equipped with a fixed support head (5), and a hobbing cutter (6) is fitted between the fixed support head (5) and the sliding kit (4).

2. The tool holder assembly of a CNC high-efficiency gear hobbing machine according to claim 1, characterized in that: The top transmission assembly (2) includes a power input gear (201), and a meshing gear (202) meshes at the bottom of the power input gear (201). A mounting shaft (203) is fixedly mounted on the side of the meshing gear (202) near the adjusting screw (7). A power transmission spline (204) is fitted on the outer wall of the mounting shaft (203).

3. The tool holder assembly of a CNC high-efficiency gear hobbing machine according to claim 1, characterized in that: The sliding kit (4) includes a movable housing (401) with a clamping spindle (404) rotatably connected inside the movable housing (401).

4. The tool holder assembly of a CNC high-efficiency gear hobbing machine according to claim 3, characterized in that: The clamping spindle (404) has a sealed annular hydraulic cavity (4045) inside, and the annular hydraulic cavity (4045) is filled with hydraulic oil. The clamping spindle (404) is also provided with a parallel spiral inertial microtube (4047) and a high-frequency overflow channel (4046), and both the spiral inertial microtube (4047) and the high-frequency overflow channel (4046) are connected to the annular hydraulic cavity (4045). A disc spring valve (40411) is provided inside the high-frequency overflow channel (4046). When the clamping spindle (404) is subjected to radial excitation force and generates relative displacement, the hydraulic oil in the annular hydraulic chamber (4045) is pressurized and selectively flows through the spiral inertial microtube (4047) or the high-frequency overflow channel (4046).

5. The tool holder assembly of a CNC high-efficiency gear hobbing machine according to claim 4, characterized in that: The disc spring valve (40411) is configured as a mechanical friction valve. The opening pressure threshold of the disc spring valve (40411) is matched with the pressure generated by the hydraulic oil when the clamping spindle (404) experiences high-frequency chatter, so as to open the high-frequency overflow channel (4046) under high-frequency and high-pressure conditions.

6. The tool holder assembly of a CNC high-efficiency gear hobbing machine according to claim 3, characterized in that: The fixed support head (5) is rotatably connected to a center sleeve. One end of the hobbing cutter (6) is engaged and connected to the clamping spindle (404). The other end of the hobbing cutter (6) is rotatably inserted into the center sleeve.

7. The tool holder assembly of a CNC high-efficiency gear hobbing machine according to claim 4, characterized in that: The outer wall of the clamping spindle (404) is provided with an oil injection hole, which is connected to the annular hydraulic chamber (4045), and the oil injection hole is internally threaded and sealed with a sealing plug. The annular hydraulic chamber (4045) is also fixedly equipped with an elastic compensating element for compensating for the thermal expansion and contraction of hydraulic oil.

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