A gantry five-axis machine tool three-axis precision optimization device
By coordinating the design of the hollow cooling screw, disc spring preload, and grating ruler assembly, the problem of reduced three-axis accuracy caused by heat accumulation during high-speed operation and long-term machining of the gantry five-axis machine tool was solved, achieving high-precision, low-noise, and long-life machining results.
Patent Information
- Application Number
- CN202522580966.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-12-04
- Publication Date
- 2026-11-03
- Estimated Expiration
- 2035-12-04
AI Technical Summary
During high-speed operation and long-term processing, the heat accumulation and temperature instability caused by the lead screw drive in the gantry five-axis machine tool lead to a decrease in repeatability and accuracy of the three-axis feed system.
The design employs a synergistic approach involving a hollow cooling lead screw, a disc spring preload assembly, and a grating ruler assembly. The hollow cooling lead screw is cooled by circulating coolant, the disc spring assembly provides preload to compensate for lead screw deformation, and the grating ruler enables fully closed-loop displacement measurement, all working together to optimize triaxial accuracy.
Effective control of lead screw temperature reduces the impact of thermal deformation, improves positioning accuracy and repeatability, extends component life, reduces noise, adapts to high-speed machining requirements, reduces scrap rate, and improves machine tool reliability and production efficiency.
Smart Images
Figure CN224927550U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of CNC machine tool technology, and more specifically, it relates to a three-axis precision optimization device for a gantry five-axis machine tool. Background Technology
[0002] As the core of high-end manufacturing equipment, the machining accuracy of the gantry five-axis machine tool directly determines the quality of key components.
[0003] In the prior art, the three axes (X / Y / Z feed axes) of this type of machine tool rely on lead screw transmission during high-speed operation and long-term machining. During high-speed movement (36m / s rapid traverse) and long-term machining, the lead screw generates a lot of heat due to friction between the lead screw and the nut and energy loss in the transmission of motor drive force. In addition, traditional lead screws do not have an effective heat dissipation structure, and heat continues to accumulate. Fluctuations in ambient temperature will further aggravate the instability of lead screw temperature, resulting in large fluctuations in repeatability positioning deviation.
[0004] Therefore, a new solution is needed to address this problem. Utility Model Content
[0005] In view of the shortcomings of the existing technology, the purpose of this utility model is to provide a three-axis accuracy optimization device for gantry five-axis machine tools by optimizing the three-axis accuracy through the collaborative design of "cooling temperature control + pre-tightening compensation + precise measurement".
[0006] This utility model achieves the above-mentioned objective through the following technical solution: a three-axis precision optimization device for a gantry five-axis machine tool, comprising three-axis feed screws distributed along the X / Y / Z axes, wherein the three-axis feed screws are configured as hollow cooling screws, and a hollow cooling component for reducing the temperature of the screws is installed on the hollow cooling screws; The hollow cooling assembly includes a hollow cooling rotary joint and an oil cooler. The two ends of the hollow cooling rotary joint are respectively sealed and connected to the central hole of the hollow cooling screw and the pipeline of the oil cooler to form a closed-loop coolant circulation path.
[0007] The present invention is further configured to include a lead screw preload assembly, wherein the lead screw preload assembly includes a disc spring, the disc spring is fitted onto the tail end of the hollow cooling lead screw, and one end abuts against the lead screw tailstock of the machine tool bed, and the other end abuts against the shoulder of the hollow cooling lead screw.
[0008] The present invention is further configured such that: two disc springs are provided, and their concave surfaces are stacked opposite each other.
[0009] The present invention is further configured to include a displacement measuring component, the displacement measuring component including a grating ruler, the body of the grating ruler being fixed to the side of the slide, the reading head being fixed to the machine tool bed, and the signal output terminal of the grating ruler being electrically connected to the machine tool CNC system.
[0010] The present invention is further configured such that: the hollow cooling assembly also includes a pipeline for conveying coolant, and the pipeline is sealed to the hollow cooling rotary joint and the oil cooler.
[0011] Compared with the prior art, the beneficial effects of this utility model are: Firstly, the hollow cooling assembly effectively controls the temperature rise of the lead screw, reducing the impact of thermal deformation on the lead screw length and avoiding displacement deviation caused by temperature fluctuations; the disc spring preload assembly can compensate for the lead screw's extension and contraction and deformation under stress, maintaining a stable gap between the lead screw and the nut and reducing backlash error; the grating ruler assembly realizes full closed-loop displacement measurement, directly feeding back the actual position and compensating for transmission chain errors such as pitch and thermal deformation in real time, jointly ensuring the three-axis positioning accuracy and repeatability accuracy, meeting the needs of high-precision parts processing; Secondly, the disc spring preload assembly stabilizes the preload force, ensuring a tight fit between the lead screw and tailstock, reducing elastic deformation of the lead screw and improving its overall rigidity. At the same time, the disc spring absorbs vibration and cutting vibration during high-speed operation, reducing machine tool noise, preventing slide displacement and surface chatter caused by vibration, and improving the quality of the machined surface. Thirdly, the hollow cooling assembly reduces material fatigue and wear of the lead screw caused by high temperature through temperature control, and the buffering effect of the disc spring can prevent the lead screw and nut from being damaged by instantaneous overload impact. Together, they reduce the wear of mechanical parts; the grating ruler assembly reduces the excessive dependence on the accuracy of the transmission chain, optimizes the stress structure of the machine tool, further extends the service life of core components such as lead screw, nut, and guide rail, as well as the whole machine, and reduces the frequency of maintenance. Fourth, the fully closed-loop control and multi-axis synchronous position feedback function enable the machine tool to accurately coordinate multi-axis linkage motion, adapting to the machining needs of complex curved surface parts such as impellers and aircraft engine blades; the improvement of high precision and stability reduces the scrap rate caused by machining errors and lowers production costs; at the same time, the structural design is adapted to high-speed feed scenarios, taking into account both machining accuracy and efficiency, and meeting the diverse machining needs of aerospace, automotive manufacturing, 3C electronics and other fields. Fifth, the grating ruler assembly can serve as an auxiliary means of machine tool condition monitoring. By analyzing the characteristics of its feedback signals, it can promptly detect potential faults such as guide rail wear and lead screw abnormalities, providing a basis for predictive maintenance, avoiding production losses caused by sudden shutdowns, and improving the reliability of machine tool operation and production continuity. Attached Figure Description
[0012] Figure 1 This is a schematic diagram of the structure of the present invention. Figure 1 ; Figure 2 This is a schematic diagram of the structure of the present invention. Figure 2 .
[0013] Reference numerals: 1. Disc spring; 2. Head; 3. Hollow cooling lead screw; 4. Hollow cooling rotary joint; 5. Slide; 6. Grating ruler. Detailed Implementation
[0014] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings. In the description of the present utility model, it should be understood that the terms "upper," "lower," "front," "rear," "left," "right," "top," "bottom," "inner," and "outer," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing the present utility model and simplifying the description. They 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 the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present utility model. Example
[0015] A three-axis precision optimization device for a gantry five-axis machine tool, such as Figures 1-2 As shown, it includes three-axis feed screws distributed along the X / Y / Z axes. The three-axis feed screws are configured as hollow cooling screws 3, wherein the hollow cooling screw 3 is made of 40CrNiMoA, with a length of 1267mm, an outer diameter of 50mm, an inner diameter of 20mm, a pitch of 10mm, and a coefficient of thermal expansion of 12×10⁻⁻⁻⁶. 6 / ℃; The hollow cooling screw 3 is equipped with a hollow cooling assembly for reducing the screw temperature. The hollow cooling assembly includes a hollow cooling rotary joint 4 and an oil cooler. The two ends of the hollow cooling rotary joint 4 are respectively sealed and connected to the central hole of the hollow cooling screw 3 and the pipeline of the oil cooler to form a closed-loop coolant circulation path. Thus, the hollow cooling screw 3 can effectively reduce its temperature through the circulation of the internal coolant. During high-speed machining or long-term operation, the hollow cooling screw 3 generates heat, leading to thermal expansion. The hollow cooling screw 3 can control the temperature at a stable level, reducing deformation caused by temperature differences, thereby improving the machining accuracy of the machine tool.
[0016] At a triaxial rapid traverse speed of 36 m / s, the temperature rise of a conventional lead screw is 20–30 °C, and its thermal elongation is: ΔL=ρ·θ·L=12×10-6 / ℃×30℃×1267mm=0.45612mm At a triaxial rapid traverse speed of 36 m / s, the temperature rise of the hollow cooling screw 3 is 4–5 °C, and its thermal elongation is: ΔL=ρ·θ·L=12×10-6 / ℃×5℃×1267mm=0.07602mm.
[0017] At the same time, an oil cooler with a temperature of 0.5℃ is selected. According to the temperature fluctuation formula: ∆T fluctuation = ∆T environment × fluctuation coefficient = 5℃ × 0.1 = 0.5℃, the temperature fluctuation of the hollow cooling screw 3 is guaranteed to be between 0.5℃ and 1℃, so that the temperature of the hollow cooling screw 3 remains relatively stable and the impact of temperature fluctuation on machining accuracy is reduced.
[0018] Furthermore, excessively high temperatures accelerate the wear of the lead screw, especially under high-speed and high-load machining conditions. The hollow cooling lead screw 3 effectively dissipates heat, reducing the temperature of the lead screw, decreasing material fatigue and wear caused by high temperatures, and thus extending the service life of the lead screw.
[0019] Long-term temperature changes can lead to thermal fatigue of the lead screw material. Hollow cooling components can reduce such temperature changes, lower the risk of thermal fatigue, and further extend the service life of the lead screw.
[0020] Furthermore, the hollow cooling assembly also includes pipelines for conveying coolant. The pipelines are sealed to the hollow cooling rotary joint 4 and the oil cooler. The pipelines ensure stable circulation of coolant, thereby ensuring stable cooling effect.
[0021] The system also includes a lead screw preload assembly, which consists of a disc spring 1. The disc spring 1 is fitted onto the tail end of the hollow cooling lead screw 3, with one end abutting against the lead screw tailstock of the machine tool bed and the other end abutting against the shoulder of the hollow cooling lead screw 3. During operation, the hollow cooling lead screw 3 may expand or contract due to thermal expansion and contraction or deformation under stress, causing it to sag and then rise. The preload generated by the elastic deformation of the disc spring 1 effectively counteracts this reduction in preload caused by expansion and contraction, ensuring that the hollow cooling lead screw 3 maintains relatively stable straightness during machining, thereby guaranteeing the machining accuracy of the machine tool.
[0022] Furthermore, the preload ensures tight contact between the hollow cooling lead screw 3 and components such as the tailstock, reducing elastic deformation and increasing rigidity. The preload also reduces bending deformation caused by thermal deformation of the hollow cooling lead screw 3. This bending deformation affects the transmission and machining accuracy of the hollow cooling lead screw 3; the compensating effect of the disc spring 1 effectively reduces this impact, improving the machining quality and stability of the machine tool.
[0023] Furthermore, during machine tool operation, especially during high-speed feed or rapid positioning, the hollow cooling lead screw 3 is subjected to significant vibration and impact. The disc spring 1 can absorb this vibration and impact energy, reducing damage to the lead screw and other machine tool components, lowering machine tool noise, and improving the machining accuracy and surface quality of the machine tool.
[0024] Meanwhile, the buffering effect of disc spring 1 can protect the lead screw and nut from excessive instantaneous load impact, prevent the lead screw and nut from being damaged due to excessive vibration, extend the service life of the lead screw and nut, and improve the reliability and stability of the machine tool.
[0025] In a machine tool's feed system, the backlash of the leadscrew affects machining accuracy. The preload of disc spring 1 can reduce the backlash of the leadscrew, improving the machine tool's positioning accuracy and repeatability, which is crucial for high-precision machining and the machining of complex parts. Furthermore, by providing preload and damping, disc spring 1 can reduce wear between the leadscrew and components such as the tailstock. This wear reduction extends the service life of components, lowers machine tool maintenance costs, and improves the machine tool's reliability and lifespan.
[0026] Simultaneously, two disc springs 1 are configured, with their concave surfaces overlapping to form a mating combination. After the two disc springs 1 are stacked in opposite directions, the "dynamic adjustment range" of elastic deformation is wider while maintaining the total preload constant. When the lead screw extends, the combined disc springs 1 can absorb the elongation through slight synchronous compression; when the lead screw retracts, the combined disc springs 1 can supplement the preload through elastic rebound, always maintaining the gap between the lead screw and the nut stable at ≤0.001mm, avoiding accuracy deviations caused by sudden changes in preload.
[0027] Compared to using a single disc spring 1, to achieve the preset preload, the single disc spring 1 needs to be compressed to a fixed deformation amount. However, when the lead screw experiences "micro-expansion / contraction" due to residual thermal elongation / stress deformation, such as 0.01~0.02mm, the deformation of the single disc spring 1 will exceed the design compression amount, causing significant fluctuations in the preload. It will either be too loose, resulting in increased clearance, or too tight, leading to overload of the lead screw's rigidity. Therefore, the concave surfaces of the disc spring 1 are relatively stacked to stabilize the preload and adapt to the dynamic compensation of the lead screw's micro-expansion / contraction.
[0028] Meanwhile, the total load-bearing capacity of the stacked disc springs 1 is twice that of a single disc spring 1. Its mechanical characteristics are: when stacked, the two disc springs 1 share the axial load, and the load is evenly distributed between the two. The total load-bearing capacity = the load-bearing capacity of a single disc spring × 2. This is crucial for the stability of the machine tool's three-axis high-speed operation.
[0029] Meanwhile, the load limit of a single disc spring 1 is fixed, such as a maximum load of 10N per disc. When the lead screw starts and stops at high speed or when the cutting load impacts, the axial instantaneous load may reach 8 to 12N. Overload can easily cause permanent deformation of disc spring 1, that is, loss of elasticity, and loss of preload compensation ability, which will lead to the expansion of lead screw clearance.
[0030] With the overall load-bearing capacity improved, the combined disc spring 1 can easily withstand the instantaneous load and cutting impact of high-speed operation, such as a maximum load of 20N for the two combined disc springs, thus avoiding overload failure of disc spring 1. At the same time, the load is evenly distributed between the two disc springs, and the stress of a single disc spring 1 is only 1 / 2 of that of a single design, which greatly reduces the risk of material fatigue and extends the stabilization period of preload compensation.
[0031] Meanwhile, when the lead screw of the overhead gantry five-axis machine tool is running at high speed, a "small off-center load" non-pure axial force will be generated due to the parallelism error of the guide rail and the radial component of the cutting force. The combined disc spring 1 is far superior to the single disc spring 1 in resisting off-center load and maintaining the uniformity of force. The single disc spring 1 has a sheet-like structure. If it is subjected to radial off-center load, it is prone to "tilting deformation". That is, the edge of the disc spring 1 is not in contact with the lead screw tailstock, resulting in an unbalanced distribution of preload. As a result, the preload on one side of the lead screw is too large, which aggravates wear, while the preload on the other side is too small, which leads to the expansion of the gap and eventually causes the lead screw to bend and the machining accuracy to decrease.
[0032] After the concave surfaces of the two disc springs 1 are stacked together, they form a "symmetrical force structure". The radial off-center load will be offset by the opposing elastic forces of the two disc springs 1, ensuring that the preload is evenly distributed along the screw axis. At the same time, the "radial stiffness" of the combined structure is improved. That is, the single disc spring 1 is easy to deform radially, but after being combined, they support each other, which can prevent the disc springs 1 from tilting and ensure that the tail end of the screw is always in a "coaxial preload state", maintaining the straightness accuracy of the screw.
[0033] Simultaneously, it exhibits better vibration damping performance, absorbing impact vibrations from high-speed operation. Because during high-speed rapid traverse of the three axes of a machine tool (36 m / s) or cutting operations, the lead screw generates high-frequency vibrations, such as 100–500 Hz. If this vibration is transmitted to the slide 5 and the machine head 2, it will cause chatter marks on the machined surface, i.e., an increase in the Ra value. The vibration damping characteristics of the combined disc spring 1 are significantly better than those of a single disc spring 1. Defects of single disc spring 1: The contact area between single disc spring 1 and lead screw tailstock is small, with only a single edge in contact. Vibration energy is difficult to dissipate through frictional damping, and most of the vibration will be directly transmitted to the lead screw and slide 5, aggravating component wear and accuracy fluctuations.
[0034] Advantages of the combined design: After the two disc springs 1 are stacked, the contact surface increases, that is, double contact is formed between the disc springs 1 and between the disc springs 1 and the tailstock. During vibration, the slight relative sliding of the two disc springs 1 will generate "friction damping", which can absorb 30% to 50% of the high-frequency vibration energy. At the same time, the "elastic recovery speed" of the combined disc springs 1 is smoother, which can buffer instantaneous impacts, such as the inertial force of high-speed start and stop, and avoid displacement deviation of the slide 5 caused by vibration.
[0035] Furthermore, from a long-term usage perspective, the service life of the combined disc spring 1 is 1.5 to 2 times that of the single disc spring 1, and its reliability is superior, directly reducing machine tool maintenance costs. Defects of single disc spring 1: Single disc spring 1 bears axial load and off-center load for a long time, and the material fatigues quickly. It usually needs to be replaced every 6 to 12 months. If it fails due to overload or off-center load, it will cause the lead screw clearance to expand and the accuracy to drop sharply. It will be necessary to stop the machine for replacement, which will affect production efficiency.
[0036] Advantages of the combined design: even load distribution and anti-eccentric load design significantly reduce the fatigue stress of individual disc springs 1 and extend their service life; even if one disc spring 1 is slightly damaged due to an accident, the other can still maintain the basic preload, and the total preload will not disappear instantly, avoiding "sudden precision failure" and leaving buffer time for maintenance; the stability of the combined structure extends the replacement cycle of disc spring 1 to 18-24 months and reduces maintenance costs by more than 50%.
[0037] Therefore, as can be seen from the above, the design of a single disc spring 1 can only meet the "static preload" requirement, while the three-axis operation of the machine tool is a complex working condition of "high speed + dynamic load + micro-extension". The combined disc spring 1, with its characteristics of "stable preload, doubled load, anti-eccentric load, strong damping, and long life", is perfectly adapted to this dynamic working condition, ensuring that the lead screw is always in a state of "stable preload, uniform force, and controllable vibration", providing a reliable "preload compensation basis" for the three-axis precision optimization structure.
[0038] The three-axis precision optimization device for a gantry five-axis machine tool also includes a displacement measurement component. The displacement measurement component includes a grating ruler 6, the body of which is fixed to the side of the slide 5, and the reading head is fixed to the machine tool bed. The grating ruler 6 can directly measure the actual displacement of the three axes of the machine tool, instead of determining the position indirectly by measuring motor speed as in traditional encoders. This allows the machine tool to change from a semi-closed loop to a fully closed loop, thereby avoiding position deviations caused by transmission chain errors such as lead screw wear, backlash, and thermal deformation. This provides more accurate position feedback to the CNC system, enabling the machine tool to execute machining instructions more precisely and improve the dimensional accuracy of machined parts.
[0039] Furthermore, the signal output terminal of the grating ruler 6 is electrically connected to the CNC system of the machine tool, enabling real-time compensation for machine tool backlash errors, lead screw pitch errors, thermal deformation errors, etc. For example, after the machine tool has been machining for a period of time, the lead screw may elongate due to thermal expansion, causing a deviation in the machining position. The grating ruler 6 can detect this change and feed the information back to the CNC system. Based on this, the system issues compensation commands to keep the machining accuracy of the machine tool stable. In mass production, the machine tool needs to repeatedly machine the same parts. The grating ruler 6 can ensure that the machine tool can accurately return to the same starting position each time, thereby ensuring the consistency of each part. This is crucial for standardized production in industries such as automobile manufacturing and 3C electronics.
[0040] Meanwhile, traditional CNC machine tools mostly use semi-closed-loop control, which indirectly controls the movement of the machine tool by measuring the rotation angle of the motor shaft. However, after installing the linear encoder 6, a fully closed-loop control system can be formed, which directly measures the actual position of the machine tool's worktable or cutting tool, eliminating the influence of transmission chain errors on machining accuracy. This significantly improves the dynamic performance and machining accuracy of the machine tool, enabling it to better meet the needs of high-speed and high-precision machining.
[0041] The grating ruler 6 has a high response frequency and resolution, which can quickly and accurately feed back the position changes of the three axes of the machine tool to the CNC system, enabling the system to achieve smoother acceleration and deceleration control, reduce overshoot and vibration, thereby improving surface finish and balancing machining accuracy and efficiency.
[0042] Modern CNC machine tools often feature multi-axis linkage capabilities for machining complex curved surface parts. The linear encoder 6 provides synchronous position feedback on each coordinate axis, ensuring precise coordination of multi-axis movements and enabling the machine tool to efficiently and precisely machine complex spatial curved surface parts such as impellers and propellers.
[0043] Because the grating ruler 6 can improve machining accuracy and stability, reduce machining defects and scrap caused by machine tool errors, improve product qualification rate, and reduce production costs, its economic benefits are even more significant when machining high-precision, high-value parts.
[0044] The application of the grating ruler 6 reduces the over-reliance on the precision of machine tool mechanical transmission components, allowing designers to optimize machine tool structure, reduce transmission links, thereby improving the rigidity and response speed of the machine tool, reducing the wear of mechanical components, and extending the service life of the machine tool.
[0045] The grating ruler 6 can be used not only for position feedback but also as a means of machine tool condition monitoring. By analyzing the feedback signal characteristics of the grating ruler 6, potential faults such as guide rail wear and lead screw abnormalities can be identified, enabling predictive maintenance, avoiding losses caused by sudden downtime, and improving the reliability of the machine tool.
[0046] In the machining of some high-precision, complex-shaped parts, such as aircraft engine blades and wing structural components in the aerospace field, the grating ruler 6 can ensure that the machine tool accurately executes machining instructions under high-speed and high-precision motion, meeting the strict requirements of these complex parts for machining accuracy, and enabling the machine tool to handle more difficult machining tasks.
[0047] The installation and use of the linear encoder 6 are relatively flexible, and can be adjusted and optimized according to different processing requirements and machine tool conditions. For example, by adjusting parameters such as the resolution and installation position of the linear encoder 6, the accuracy requirements of specific processing tasks can be met, thereby improving the adaptability and flexibility of the machine tool.
[0048] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this invention. No reference numerals in the claims should be construed as limiting the scope of the claims.
[0049] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.
Claims
1. A three-axis precision optimization device for a gantry five-axis machine tool, comprising three-axis feed screws distributed along the X / Y / Z axes, characterized in that, The three-axis feed screw is configured as a hollow cooling screw (3), and a hollow cooling assembly for reducing the temperature of the screw is installed on the hollow cooling screw (3); The hollow cooling assembly includes a hollow cooling rotary joint (4) and an oil cooler. The two ends of the hollow cooling rotary joint (4) are respectively sealed and connected to the center hole of the hollow cooling screw (3) and the pipeline of the oil cooler to form a closed-loop coolant circulation path.
2. The three-axis accuracy optimization device for a gantry five-axis machine tool according to claim 1, characterized in that: It also includes a lead screw preload assembly, which includes a disc spring (1). The disc spring (1) is fitted onto the tail end of the hollow cooling lead screw (3), with one end abutting the lead screw tailstock of the machine tool bed and the other end abutting the shoulder of the hollow cooling lead screw (3).
3. The three-axis accuracy optimization device for a gantry five-axis machine tool according to claim 2, characterized in that: The disc spring (1) is configured as two, with the concave surfaces overlapping each other.
4. The three-axis accuracy optimization device for a gantry five-axis machine tool according to claim 1, characterized in that: It also includes a displacement measuring component, which includes a grating ruler (6). The body of the grating ruler (6) is fixed to the side of the slide (5), the reading head is fixed to the machine tool bed, and the signal output end of the grating ruler (6) is electrically connected to the machine tool CNC system.
5. The three-axis precision optimization device for a gantry five-axis machine tool according to claim 1, characterized in that: The hollow cooling assembly also includes a pipeline for conveying coolant, and the pipeline is sealed to the hollow cooling rotary joint (4) and the oil cooler.