Centrifugal feed face cutter for boring of ship moon-shaped boss

Abstract

The application discloses a centrifugal feeding plane tool rest for boring a crescent boss of a ship, which comprises a tool rest main body and a mounting base at one end of the tool rest main body, and a slide rail is arranged on the tool rest main body; a tool mounting frame with a mounting groove is slidably arranged on the slide rail. A feeding linkage rod is arranged on the tool rest main body, the feeding linkage rod comprises a screw rod and a centrifugal slide rod arranged coaxially, the tool mounting frame is sleeved on the screw rod, and a centrifugal driving assembly is sleeved on the centrifugal slide rod. The centrifugal driving assembly comprises a centrifugal slide block, an elastic telescopic guide rod is arranged on the centrifugal slide block, a spiral groove, which is in communication with a spiral feeding section and a linear returning section, is formed in the centrifugal slide rod, the end of the guide rod is always in contact with the bottom surface of the spiral groove, and an elastic member is arranged between the centrifugal slide block and the tool rest main body. The centrifugal force generated by the rotation of the tool rest is utilized to drive feeding, the path selection of the spiral groove is utilized, automatic feeding during high-speed rotation of a non-cutting section and stable cutting during low-speed rotation of a cutting section are realized, and the structure is simple and does not need external power.

Description

Technical Field

[0001] This invention relates to the field of machining equipment technology, specifically to a centrifugal feed planar tool holder for boring crescent-shaped bosses in ships. Background Technology

[0002] In shipbuilding, the installation accuracy of the rudder system is one of the key factors affecting the navigation safety and control performance of a ship. Among them, the fit clearance between the rudder blade anti-skid block and the rudder arm is particularly important—too large a clearance will cause the rudder blade to bounce, affecting navigation stability; too small a clearance may cause jamming, or even lead to safety accidents. Therefore, ship design drawings have clear tolerance requirements for the clearance of the anti-skid block.

[0003] However, during actual construction, due to accumulated errors in the hull structure and manufacturing deviations in the straightness of the cast steel rudder arm, the clearance of the anti-slip blocks is often difficult to guarantee precisely. To solve this problem, the design department has specially added a crescent-shaped boss structure at the anti-slip block installation position on the lower plane of the cast steel rudder arm on some ship types (such as the 50,000t MR oil tanker). The height of this boss is usually about 10mm. Its function is to obtain a precise reference plane by boring and flattening this boss during the boring of the rudder system, thereby ensuring that the clearance between the anti-slip block and the rudder arm remains uniform and consistent at any rotation angle of the rudder blade, meeting the design requirements.

[0004] However, this design improvement brought new technical challenges to on-site machining. The crescent-shaped boss is located on the lower plane of the cast steel rudder arm, a special machining position with limited space, and needs to be completed simultaneously with the rudder system boring process. Traditional boring equipment is mainly designed for shaft hole machining and lacks a suitable surface machining device for this condition. If a large floor-type boring and milling machine is used, not only is equipment scheduling difficult and costly, but the large size of the workpiece also makes precise positioning and clamping difficult. If handheld grinding or milling tools are used, machining accuracy and surface quality are difficult to guarantee, and quality problems such as out-of-tolerance flatness and vibration marks are likely to occur.

[0005] In view of the above-mentioned working conditions, there is a need in the art for a planar machining device that can be easily installed on a boring bar, is lightweight, and is easy to operate. The device should be able to rotate with the boring bar spindle to achieve the boring and flattening of crescent-shaped bosses at specific locations, and should also have a reliable feed mechanism to ensure that the flatness and roughness of the machined surface meet the design requirements. Summary of the Invention

[0006] The purpose of this invention is to overcome the defects existing in the prior art and provide a centrifugal feed planar tool holder for boring crescent-shaped bosses in ships.

[0007] To achieve the above objectives, the technical solution of this invention is to design a centrifugal feed planar tool holder for boring crescent-shaped bosses in ships, comprising a tool holder body and a mounting base disposed at one end of the tool holder body. A slide rail is provided on the tool holder body, and a tool mounting bracket is slidably fitted onto the slide rail. The tool mounting bracket has a mounting groove, in which a tool is mounted. A feed linkage rod is also mounted on the tool holder body via a bearing, and the tool mounting bracket is fitted onto the feed linkage rod. A centrifugal drive assembly is also fitted onto the feed linkage rod. By providing a feed linkage rod threadedly fitted to the tool mounting bracket on the tool holder body, and fitting a centrifugal drive assembly driven by centrifugal force onto the feed linkage rod, the centrifugal force generated by the rotation of the tool holder is converted into the power to drive the feed linkage rod to rotate, thereby driving the tool mounting bracket to perform radial feed motion along the slide rail. This structure cleverly utilizes the rotation of the tool holder itself as a power source, achieving automatic feed without the need for external energy or a complex control system. The mounting base is used to fix the entire tool post to the boring machine spindle or flange, ensuring that the tool post can rotate with the spindle.

[0008] Furthermore, the feed linkage includes a lead screw and a centrifugal slide rod arranged coaxially. The tool mount is fitted onto the lead screw, and the centrifugal drive assembly is fitted onto the centrifugal slide rod. The feed linkage consists of two parts: the lead screw and the centrifugal slide rod. The lead screw is responsible for accurately converting the rotational motion into the linear feed motion of the tool mount, while the centrifugal slide rod, together with the centrifugal drive assembly, realizes the feed under centrifugal force. Their coaxial arrangement ensures smooth power transmission and a compact structure.

[0009] Furthermore, the centrifugal drive assembly includes a centrifugal slider mounted on a centrifugal slide rod. The centrifugal slide rod has a helical groove, and the centrifugal slider has a guide rod that slides in conjunction with the helical groove. An elastic element is provided between the centrifugal slider and the tool holder body or slide rail. The guide rod is an elastic, telescopic rod, and its end is always in contact with the bottom surface of the helical groove. When the tool holder rotates, the centrifugal slider is subjected to centrifugal force, overcoming the preload of the elastic element, and slides radially outward along the centrifugal slide rod. As the guide rod, fixed to the centrifugal slider, moves radially, its end, constrained by the sidewall of the helical groove, forces the centrifugal slide rod to rotate. This rotational motion is transmitted to the tool mounting bracket via a coaxial lead screw, achieving feed. The elastic element provides a restoring force, causing the centrifugal slider to return to its original position when the centrifugal force decreases (e.g., the rotational speed decreases) or disappears. The guide rod is designed as an elastic, telescopic rod and always in contact with the bottom surface of the helical groove. This ingenious design allows the guide rod to move along paths with different groove depths, making unidirectional intermittent feed possible.

[0010] Furthermore, the spiral groove includes a spiral feed section and a first end to a first end of the spiral feed section, as well as a straight return section and a second end to a second end of the straight return section. The first end is connected to the second end, and the groove depth at the first end is deeper than that at the second end. The first end is connected to the second end, and the groove depth at the first end is shallower than that at the second end. The entire spiral groove is a closed loop path in which the guide rod runs. The spiral feed section is used to drive the feed, while the straight return section is used for rapid reset and does not generate feed. Setting different groove depths ensures that during feeding, the guide rod can only travel through the spiral feed section, and during return, the guide rod can only travel through the straight return section.

[0011] Optionally, the groove depth gradually decreases from the first end to the first end of the spiral feed section. This gradually decreasing groove depth, combined with the elastic and retractable guide rod, forms a unidirectional drive mechanism similar to a ratchet.

[0012] Optionally, in a preferred embodiment of the invention, the groove depth gradually increases from the second beginning end to the second end end of the straight return segment.

[0013] Furthermore, in a preferred embodiment of the present invention, the groove width W of the spiral groove and the diameter d of the guide rod satisfy the following condition: 1.05d ≤ W ≤ 1.10d, and the two side walls of the spiral groove have a draft angle of 10 to 15 degrees. The appropriate clearance ensures smooth sliding of the guide rod within the groove, preventing jamming. The draft angle design of the side walls facilitates machining, and more importantly, it allows the formation of a wedge-shaped oil film when the guide rod contacts the groove wall, promoting lubrication, reducing frictional resistance, and making the sliding of the guide rod within the groove more sensitive and reliable, thus improving the response speed of the tool holder to changes in centrifugal force.

[0014] Furthermore, the lead P of the leadscrew and the lead p of the helical feed section satisfy the following relationship: p = kP, where k is a constant ranging from 15 to 50. The lead p of the helical feed section determines the angle through which the centrifugal slide rod rotates per unit radial distance the centrifugal slider moves. The lead P of the leadscrew determines the radial feed amount of the tool corresponding to this angle. By appropriately selecting the value of k (i.e., the transmission ratio), a large radial displacement of the centrifugal slider can be converted into an extremely small amount of tool feed, thereby achieving high-precision cutting. The larger the value of k, the finer the feed.

[0015] Furthermore, the travel path of the linear return segment is parallel to the axis of the centrifugal slide bar. Designing the return segment parallel to the axis ensures that during the return process, regardless of the movement of the guide rod within the slot, no circumferential driving torque is generated on the centrifugal slide bar. This guarantees a complete stop of the tool feed in the non-cutting section, achieving the intended function of "cutting feed, non-cutting stop".

[0016] Furthermore, the spiral feed section has a 360-degree orbital angle. Designing the spiral feed section to orbit the centrifugal slide bar once (360 degrees) means that for every complete radial movement of the centrifugal slide bar (from the smallest radius to the largest radius, corresponding to the groove from deepest to shallowest), it drives the centrifugal slide bar to rotate one revolution. This rotation is converted into a lead of tool feed rate via a leadscrew. This design establishes a clear correspondence between the feed rate and the centrifugal slide bar displacement, facilitating understanding and design calculations.

[0017] The advantages and beneficial effects of this invention are as follows: Through the ingenious cooperation between the centrifugal drive assembly and the feed linkage rod with a specially shaped helical groove, the matching of feed action and machining is automatically achieved. Automatic feed occurs during high-speed rotation in the non-cutting section, and automatic stop and stable cutting occur during low-speed rotation in the cutting section. This optimized cycle can be achieved without any sensors, controllers, or external power. The feed action is completed only during the high-speed rotation in the non-cutting section, avoiding vibration and surface defects that may result from simultaneous feed motion during cutting. Maintaining a stable low-speed rotation and a fixed cutting depth in the cutting section yields extremely high flatness and surface finish. By rationally designing the transmission ratio (k value), the feed per revolution can be controlled at the micrometer level, meeting the machining requirements of high-precision ship components. This tool holder structure allows for high-speed rotation in the non-cutting section, quickly completing the feed action and rapidly completing the idle stroke; while in the cutting section, the optimal cutting speed is used to ensure cutting efficiency and quality. This "high-speed feed, low-speed cutting" mode ensures machining quality in the cutting section while minimizing auxiliary time in the non-cutting section, comprehensively improving machining efficiency. The entire automatic feed mechanism is composed entirely of mechanical parts, without any complex electrical, hydraulic, or pneumatic components. This makes the tool holder structure exceptionally simple, compact, and inexpensive to manufacture. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the tool holder of the present invention in use; Figure 2 This is a schematic diagram of the tool holder structure of the present invention; Figure 3 This is a cross-sectional view of the centrifugal drive assembly of the present invention; Figure 4 This is a schematic diagram of the centrifugal slide bar of the present invention; Figure 5 This is a schematic diagram of the feed linkage rod of the present invention.

[0019] In the diagram: 1. Mounting base; 2. Slide rail; 3. Tool mounting bracket; 4. Mounting slot; 5. Tool; 6. Feed linkage rod; 7. Centrifugal drive assembly; 61. Lead screw; 62. Centrifugal slide bar; 71. Centrifugal slider; 63. Spiral groove; 711. Guide rod; 72. Elastic element; 631. Spiral feed section; 6311. First starting end; 6312. First ending end; 632. Linear return section; 6321. Second starting end; 6322. Second ending end. Detailed Implementation

[0020] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings and examples. The following examples are only used to more clearly illustrate the technical solutions of the present invention and should not be construed as limiting the scope of protection of the present invention.

[0021] This invention is a centrifugal feed planar tool holder for boring crescent-shaped bosses on ships. This tool holder is specifically designed for machining crescent-shaped bosses on ship components on boring machines or similar rotary machine tools. It can utilize the difference in centrifugal force generated by the change in rotation speed of the tool holder at different machining stages to achieve automatic intermittent feed linked to the rotation speed.

[0022] like Figure 1 As shown, the planar tool post mainly includes a tool post body and a mounting base 1 located at one end of the tool post body. The mounting base 1 is the mounting base of the entire tool post, and its structure needs to match the connecting flange of the boring machine spindle. Multiple bolt holes are evenly distributed around its circumference. Through these bolt holes, high-strength bolts can be used to firmly fix the entire tool post to the end flange of the boring machine spindle, ensuring that the tool post can rotate accurately and smoothly with the spindle. The connection between the mounting base 1 and the tool post body can be integrally formed or fastened with high-strength screws to ensure overall rigidity. A slide rail 2 is provided on the tool post body. The slide rail 2 is a guide mechanism that guides the tool for radial feed. To obtain high rigidity and high-precision guidance, the slide rail 2 is composed of a pair of parallel high-precision linear guide rails. The track portion of the linear guide rail is fixedly mounted on the tool post body, while the slider portion is fixedly connected to the tool mounting bracket 3. The tool mounting bracket 3 is slidably fitted onto the slide rail 2. The tool mounting bracket 3 is a component used to install and fix the tool 5. Its bottom is fixedly connected to the slider of the slide rail 2, allowing it to reciprocate linearly along the slide rail 2. The tool mounting bracket 3 has a mounting groove 4 on its top or side. The mounting groove 4 is designed as a combination of a V-shaped groove and a pressure plate to quickly and securely clamp tools 5 of different sizes of square tool holders. The tool 5 is fixed in the mounting groove 4 by the pressure plate and screws, and the radial position of its tip can be initially set by adjusting the extension of the tool 5 in the mounting groove 4.

[0023] The tool post body also features a feed linkage 6 mounted via bearings. The bearings (not shown in detail in the figure) are installed within bearing housings on the tool post body, supporting the feed linkage 6 and allowing it to rotate freely relative to the tool post body while bearing radial and axial loads. The feed linkage 6 is the core transmission component for achieving feed in this tool post. Figure 5 As shown, the feed linkage 6 includes a lead screw 61 and a centrifugal slide rod 62, which are coaxially arranged and fixedly connected as one unit. The lead screw 61 is located on the side closer to the tool mount 3, and the centrifugal slide rod 62 is located on the side farther from the tool mount 3. The two are connected by a coupling or directly machined as a single unit to ensure coaxiality. The tool mount 3 is fitted onto the lead screw 61. Specifically, the tool mount 3 has a threaded hole inside that mates with the lead screw 61, thus forming a precision lead screw and nut pair. When the lead screw 61 rotates, it drives the tool mount 3 to move linearly along the slide rail 2.

[0024] The centrifugal drive assembly 7 is mounted on the centrifugal slide bar 62 of the feed linkage 6, and is the power conversion part of the entire automatic feed mechanism. Please refer to the relevant documentation. Figure 2 The centrifugal drive assembly 7 mainly includes a centrifugal slider 71 and an elastic element 72. The centrifugal slider 71 is a block-shaped part with a central hole that precisely fits the outer circle of the centrifugal slide rod 62, allowing the centrifugal slider 71 to slide freely along the axial direction of the centrifugal slide rod 62 and rotate with it under its drive. To achieve motion conversion between the centrifugal slider 71 and the centrifugal slide rod 62, a spiral groove 63 of a specific shape is formed on the outer cylindrical surface of the centrifugal slide rod 62. Correspondingly, a guide rod 711 is fixedly installed on the centrifugal slider 71, slidingly engaging with the spiral groove 63. A detachable counterweight is installed on the centrifugal slider 71, and the weight of the counterweight can be adjusted according to different actual rotational speeds, thereby adjusting the magnitude of the centrifugal force. When installing the counterweight, it is important to ensure the balance of the entire tool holder; it should not be installed on only one side, causing the entire tool holder to be eccentric.

[0025] like Figure 3 As shown, the guide rod 711 is designed as a flexible, telescopic rod. Its specific structure can be a rod made of spring steel, with one end fixed to the centrifugal slider 71, and the other end a miniature assembly consisting of a sleeve, a compression spring, and a push rod. The pressure of the built-in spring ensures that the end of the push rod always presses against the bottom surface of the spiral groove 63. This elastic design allows the length of the guide rod 711 to be adaptively adjusted according to the groove depth at the contact position, and its end always maintains contact with the bottom surface of the spiral groove 63, which is the basis for achieving subsequent unidirectional intermittent drive.

[0026] An elastic element 72 connects the centrifugal slider 71 to the blade holder body or slide rail 2. In this embodiment, the elastic element 72 is a cylindrical helical compression spring. One end of the spring abuts against the end face of the centrifugal slider 71, and the other end abuts against and is fixed to the slide rail 2. The preload of the elastic element 72 is used to balance the centrifugal force, and its stiffness determines the critical speed at which the centrifugal slider 71 begins to slide outward.

[0027] like Figure 4 As shown, the spiral groove 63 is a closed loop path, not a simple single line, but a combination of two groove segments with different functions. Specifically, the spiral groove 63 includes a spiral feed section 631 and a straight return section 632. For ease of description, the starting point of the spiral feed section 631 is defined as the first beginning end 6311, and the ending point is defined as the first end end 6312; the starting point of the straight return section 632 is defined as the second beginning end 6321, and the ending point is defined as the second end end 6322. These two groove segments are connected end-to-end, forming a closed loop. The connection relationship is as follows: the first beginning end 6311 is connected to the second end end 6322, and the groove depth at the first beginning end 6311 is deeper than the groove depth at the second end end 6322. At the same time, the first end end 6312 is connected to the second beginning end 6321, and the groove depth at the first end end 6312 is shallower than the groove depth at the second beginning end 6321.

[0028] To achieve the aforementioned requirements for different groove depths, the groove depth also varies systematically along the path. Firstly, the straight return section 632 has the same groove depth, while along the spiral feed section 631, from its first end 6311 to its first end 6312, the groove depth gradually decreases, transitioning from the deepest to the shallowest. At this point, the groove depth at the second end 6321 of the straight return section 632 is greater than the groove depth at the first end 6312. When the guide rod 711 reaches the second end 6321 of the straight return section 632 from the spiral feed section 631, it will pass through a step. This step restricts the guide rod 711 from returning from the first end 6312 of the spiral feed section 631. Similarly, the groove depth of the second end 6322 of the straight return section 632 is less than the groove depth of the first end 6311 of the spiral feed section 631. After the guide rod 711 reaches the second end 6322 from the second end 6321 along the straight return section 632, it will pass through the first end 6311 of the spiral feed section 631 again. This step is also to restrict the guide rod 711 from feeding from the second end 6322 of the straight return section 632.

[0029] The second method involves a spiral feed section 631 with a uniform groove depth, while the groove depth gradually increases from the second beginning 6321 to the second end 6322 of the linear return section 632. The resulting effect and working principle are the same as the first method, and will not be elaborated further here. The third method involves both the spiral feed section 631 and the linear return section 632 having different groove depths, as long as the final effect is consistent with the first method.

[0030] like Figure 3 As shown, to optimize the motion performance of the guide rod 711 within the helical groove 63, the dimensions and shape of the helical groove 63 are also limited. The groove width W of the helical groove 63 and the diameter d of the guide rod 711 satisfy: 1.05d ≤ W ≤ 1.10d. This clearance ensures that the guide rod 711 can slide freely within the groove without causing motion lag or impact due to excessive clearance. Simultaneously, the cross-section of the helical groove 63 is not rectangular; its two side walls have draft angles of 10 to 15 degrees. This design not only facilitates demolding during processing but, more importantly, ensures that the contact between the guide rod 711 and the groove wall is line contact during operation. Furthermore, this draft angle helps guide lubricant into the contact surface, forming a lubricating film, significantly reducing frictional resistance, and making the guide rod 711 more sensitive to changes in groove depth, thus improving the mechanism's response sensitivity.

[0031] like Figure 5 As shown, to precisely control the feed per revolution of the tool, key parameters of the lead screw 61 and the helical feed section 631 were designed in a related manner. Let the lead of the lead screw 61 be P, and the lead of the helical feed section 631 be p. Then, the two satisfy the relationship: p = kP, where k is a constant, and its value ranges from 15 to 50. The value of k actually represents a magnification factor. The axial displacement p corresponding to the guide rod 711 in the helical feed section 631 is converted into the rotation of the centrifugal slide rod 62 through the guidance of the helical groove, and then into the linear motion of the tool mounting bracket 3 through the lead screw 61. Since p is much larger than P, a large radial displacement of the centrifugal slide rod is reduced to a very small tool feed. For example, if k = 30 and the lead screw lead P = 2 mm, then the lead of the helical feed section 631 p = 60 mm. This means that the guide rod 711 rotates radially along the helical feed section 631 for one cycle, driving the lead screw 61 to rotate one revolution, and the tool feeds 2 mm.

[0032] The travel path of the straight return segment 632 is parallel to the axis of the centrifugal slide bar 62. This ensures that it does not generate feed in the low-speed cutting segment. When the guide rod 711 is in this segment, no matter how it slides along the groove, the force it exerts on the groove sidewall is radial, with no circumferential component, and therefore cannot drive the centrifugal slide bar 62 to rotate, and the tool feed motion stops.

[0033] Furthermore, the spiral feed section 631 is designed with a 360-degree rotation angle. This ensures that each movement of the centrifugal slider 71 drives the centrifugal slide rod 62 to complete one full rotation, corresponding to the lead screw 61 driving the tool mount 3 to feed a lead distance P. This design makes the correspondence between the feed rate and the centrifugal slider displacement intuitive and clear, facilitating precise engineering design.

[0034] The working process and principle of the planar tool post will be described in detail below, taking into account the movement of guide rod 711: Initial state: When the tool holder is stationary or at a very low speed, the spring force of the elastic element 72 is greater than the small centrifugal force on the centrifugal slider 71, pushing the centrifugal slider 71 towards the center of rotation. At this time, the guide rod 711 fixed on the centrifugal slider 71 extends to its longest length under its own elastic force, with its end abutting the deepest part of the spiral groove 63, that is, located at the first end 6311 of the spiral feed section 631 (which is also the second end 6322 of the linear return section 632). The tool mounting bracket 3 is adjusted to the initial cutting radius position by manually rotating the feed linkage rod 6 or the lead screw 61 according to the machining needs, and the tip of the tool 5 is aligned with the outer edge of the crescent-shaped boss on the workpiece.

[0035] During the non-cutting section (high-speed rotation), the spindle speed is controlled according to the machining phase as it feeds along the helical feed section 631 (centrifugal force driven). When the tool holder rotates to the position of the non-crescent-shaped boss, this is the non-cutting section, and the spindle speed is increased to a higher speed. Under high-speed rotation, the centrifugal slider 71 is subjected to a large centrifugal force, overcoming the preload of the elastic element 72, and slides radially outward along the centrifugal slide rod 62. At this time, the guide rod 711 is located at the first end 6311 of the helical feed section 631. As the centrifugal slider 71 moves outward, the guide rod 711 slides along the helical feed section 631 towards the first end 6312. Since the groove depth of the helical feed section 631 gradually becomes shallower, the radial outward movement of the guide rod 711 is restricted by the shallowing of the groove bottom, forcing the guide rod 711 to be compressed. When the guide rod 711 reaches the first end 6312 along the first end 6311 of the spiral feed section 631 (at this time, it also passes through the step to enter the second end 6321 of the linear return section 632, but remains in this position under the action of centrifugal force), the centrifugal slide rod 62 rotates one revolution. The rotation of the centrifugal slide rod 62 drives the lead screw 61, which is fixed coaxially with it, to rotate synchronously. The rotation of the lead screw 61 drives the tool mounting bracket 3, which is threaded with it, to overcome frictional resistance and make a linear feed motion along the slide rail 2 in the direction to be cut (i.e., radially outward or inward).

[0036] Because the lead p of the helical feed section 631 is much larger than the lead P of the leadscrew 61 (e.g., k=30), a relatively large radial displacement of the guide rod caused by centrifugal force is ultimately converted into an extremely small radial feed of the tool. This feed process continues in the high-speed rotating non-cutting section. When the tool holder is about to pass through the non-cutting section, the spindle speed is reduced to the optimal cutting speed. At this time, the centrifugal force decreases accordingly and becomes less than the spring force of the elastic element 72. Under the push of the elastic element 72, the centrifugal slider 71 begins to return to the center. At this time, the guide rod 711 is located at the first end 6312 and enters the second beginning end 6321 of the linear return section 632 connected to it. During the return process, the guide rod 711 slides along the linear return section 632 towards the second end 6322 and finally reaches the second end 6322 (at this time, it will pass through another step and reach the first beginning end 6311, and the centrifugal slider 71 is fully returned to the center). Since the travel path of the straight return section 632 is parallel to the axis of the centrifugal slide bar 62, the sliding of the guide rod 711 will not generate circumferential thrust on the groove wall. Therefore, the centrifugal slide bar 62 and the lead screw 61 remain stationary, the tool mounting bracket 3 does not feed, and the tool 5 performs cutting at a stable low speed.

[0037] When the tool holder re-enters the non-cutting section, the guide rod 711 has just completed its reset, reaching the deepest first end 6311, ready to begin the next high-speed feed. When the spindle speeds up again, the centrifugal force increases, and the guide rod 711 will slide along the helical feed section 631 again for the next round of feed. This cycle repeats continuously. Through the carefully designed gradient groove depth on the helical groove 63 and the cooperation of the elastic and retractable guide rod 711, this planar tool holder establishes a perfect unidirectional cycle mechanism: in the non-cutting section (high speed), centrifugal force drives the guide rod 711 along the helical feed section 631; in the cutting section (low speed), elastic force drives the guide rod to reset along the straight return section 632. The two processes do not interfere with each other and automatically switch, realizing an automatic feed machining cycle.

[0038] In summary, the centrifugal feed planar tool holder for boring crescent-shaped bosses provided by this invention, with its unique all-mechanical structure, ingeniously solves many problems in the prior art, realizing efficient, high-precision, and highly automated crescent-shaped boss planar machining, and has extremely high practical and promotional value.

[0039] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A centrifugal feed planar tool holder for boring crescent-shaped bosses in ships, characterized in that, The tool holder includes a tool holder body and a mounting base (1) located at one end of the tool holder body. The tool holder body is provided with a slide rail (2), and a tool mounting bracket (3) is slidably mounted on the slide rail (2). The tool mounting bracket (3) has a mounting groove (4) and a tool (5) is installed in the mounting groove (4). The tool holder body is also equipped with a feed linkage rod (6) via a bearing. The tool mounting bracket (3) is fitted onto the feed linkage rod (6), and a centrifugal drive assembly (7) is also fitted onto the feed linkage rod (6).

2. The centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 1, is characterized in that... The feed linkage rod (6) includes a lead screw (61) and a centrifugal slide rod (62) arranged coaxially. The tool mounting bracket (3) is mounted on the lead screw (61), and the centrifugal drive assembly (7) is mounted on the centrifugal slide rod (62).

3. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 2, is characterized in that... The centrifugal drive assembly (7) includes a centrifugal slider (71) fitted on a centrifugal slide bar (62). The centrifugal slide bar (62) has a spiral groove (63). The centrifugal slider (71) is provided with a guide rod (711) that slides with the spiral groove (63). An elastic element (72) is provided between the centrifugal slider (71) and the tool holder body or the slide rail (2). The guide rod (711) is an elastic telescopic rod. The end of the guide rod (711) is always in contact with the bottom surface of the spiral groove (63).

4. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 3, is characterized in that... The spiral groove (63) includes a spiral feed section (631) and a first end (6311) to a first end (6312) of the spiral feed section (631), and a straight return section (632) and a second end (6321) to a second end (6322) of the straight return section (632). The first end (6311) is connected to the second end (6322), and the groove depth of the first end (6311) is deeper than that of the second end (6322). The first end (6312) is connected to the second end (6321), and the groove depth of the first end (6312) is shallower than that of the second end (6321).

5. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 4, is characterized in that... The groove depth gradually decreases from the first end (6311) to the first end (6312) of the spiral feed section (631).

6. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 4, is characterized in that... The groove depth gradually increases from the second beginning (6321) to the second end (6322) of the straight return segment (632).

7. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 4, is characterized in that... The groove width W of the spiral groove (63) and the diameter d of the guide rod (711) satisfy: 1.05d≤W≤1.10d, and the two side walls of the spiral groove (63) have a draft angle of 10 to 15 degrees.

8. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 4, is characterized in that... The lead P of the lead screw (61) and the lead p of the spiral feed section (631) satisfy the following condition: p = kP, where k is a constant and its value ranges from 15 to 50.

9. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 4, is characterized in that... The travel path of the straight return segment (632) is parallel to the axis of the centrifugal slide bar (62).

10. A centrifugal feed planar tool holder for boring a crescent-shaped boss in a ship, as described in claim 4, is characterized in that... The spiral feed section (631) has a 360-degree circumference.

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