Arc-shaped cutter head of hard rock heading machine

Abstract

The invention discloses an arc-shaped hard rock heading machine cutterhead, a cutterhead structural member comprises an arc-shaped cutterhead panel, a large circular ring and the like, a hob is arranged on the cutterhead panel, a blade is arranged in an arc shape, and scrapers are distributed on the periphery of the cutterhead panel and the side part of a connecting ring. During working, the hob is driven by a rear driver to rotationally break rocks, and the scraper and the slag scraping plate cooperate to discharge slag stones; and the hob can be replaced when the cutter wear exceeds a threshold value. The cutterhead can also switch modes, the connecting ring is changed into a twisting leg structure, and the cutterhead is suitable for an earth pressure or slurry balance mode after a slag scraping plate is removed. The performance of the cutter head can be accurately controlled through formulas such as the hob rock breaking efficiency and the slag stone discharging efficiency. Compared with a traditional cutterhead, the hard rock T-joint tunnel excavation problem is solved, the excavation efficiency is improved, long-distance tunneling and multi-mode operation are achieved, and great significance is achieved for underground space construction.

Description

Technical Field

[0001] The invention belongs to the technical field of tunnel boring machines, and in particular relates to an arc-shaped hard rock tunnel boring machine cutter head. Background Art

[0002] Traditional tunnel boring machine cutterheads perform well when excavating straight tunnels with relatively uniform geological conditions. However, when encountering tunnels with unusual structures such as T-junctions, and especially when operating in hard rock formations, existing cutterhead technology presents numerous challenges. The unique geometry of T-junction tunnels requires a cutterhead capable of adapting to the curved excavation path. Conventional flat cutterheads cannot adapt well to the concave surface of T-junction tunnels, resulting in a large gap between the cutterhead and the tunnel wall during excavation. This not only affects excavation accuracy but also easily causes excessive fragmentation and collapse of the surrounding rock, increasing construction risks and costs. Furthermore, existing T-junction curved hard rock cutterheads are front-loaded and cannot be replaced, making them unsuitable for long-distance tunneling. Furthermore, existing T-junction curved cutterheads are pressure-balanced, making them unsuitable for open-type excavation.

[0003] In summary, developing a cutterhead that can adapt to the curved path of T-junction tunnels, efficiently crush hard rock, and excavate in open hard rock, and that can easily switch excavation modes, has become an urgent problem to be solved in the field of tunnel engineering. Summary of the Invention

[0004] To this end, the present invention provides an arc-shaped hard rock tunnel boring machine cutterhead to solve the problems of difficulty in cutting connecting channels in hard rock formations, inability to change cutters when tunneling long-distance connecting channels, and the inability of existing technologies to be used for hard rock open connecting channel tunnel boring machines.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a curved hard rock tunnel boring machine cutter head, comprising: The cutterhead structure includes a cutterhead panel, a large ring, a connecting ring, a flange, and a scraper plate. The cutterhead panel has an arc-shaped cross-section and is used to fit the concave arc surface of the T-junction tunnel. The hob is mounted on a hob box, the hob box is fixed on the cutter head panel, and the blade of the hob is arranged in an arc shape on the cutter head panel; The scrapers are arranged around the periphery of the cutter head panel and the side of the connecting ring.

[0006] As a preferred solution for the arc-shaped hard rock tunnel boring machine cutterhead, the cutterhead panel is connected to the large ring, the large ring is connected to the flange through the connecting ring, and the rear end of the flange is connected to the intermediate drive or the peripheral drive.

[0007] As a preferred solution for the arc-shaped hard rock tunnel boring machine cutterhead, when the tunnel boring machine starts, the blades of the adjacent rollers penetrate the soil synchronously, and the flanges are driven to rotate by the rear drive. The rotational force is transmitted to the rollers in front to rotate the rollers, thereby achieving rock crushing and completing the excavation of the face.

[0008] As an optimal solution for the arc-shaped hard rock tunnel boring machine cutterhead, after excavation is completed, the slag accumulates at the bottom of the cutterhead, and the scrapers around it scrape the slag into the scraper plate; when the cutterhead rotates, the scraper plate drives the slag upward, and after the slag reaches the set angle, it slides down through the scraper plate and enters the belt conveyor slag collection device.

[0009] As a preferred solution for the cutterhead of an arc-shaped hard rock tunnel boring machine, when the excavation length of the T-junction tunnel reaches a set value, causing the wear degree of the disc cutter and the scraper to exceed the preset tool effective use threshold range, the disc cutter is replaced.

[0010] As a preferred solution for the arc-shaped hard rock tunnel boring machine cutterhead, it also includes a twisted leg structure. When the connecting ring in the cutterhead structural component is replaced by the twisted leg structure and the scraper plate is removed, it is applied to the earth pressure balance mode or the mud water balance mode.

[0011] As a preferred solution for the cutterhead of an arc-shaped hard rock tunnel boring machine, the rock breaking efficiency of the cutter is related to the number of blades, blade shape and rotation speed of the cutter. The calculation formula of the rock breaking efficiency of the cutter is:

[0012] Where, For the rock breaking efficiency of the roller cutter, The number of blades is, is the blade shape coefficient, is the reel rotation speed.

[0013] As the preferred solution for the arc-shaped hard rock tunnel boring machine cutterhead, the slag discharge efficiency during the excavation process is related to the inclination angle of the scraper, the rotation speed of the cutterhead, and the amount of slag accumulation. The calculation formula for the slag discharge efficiency is:

[0014] Where, For the slag discharge efficiency, is the inclination angle of the scraper plate, is the cutter head rotation speed, The amount of slag accumulation.

[0015] As a preferred solution for the cutterhead of an arc-shaped hard rock tunnel boring machine, the degree of wear of the cutter is related to the excavation distance, rock hardness, and the material of the cutter. The calculation formula for the degree of wear of the cutter is:

[0016] Where, is the degree of wear of the hob, is the excavation distance, is the rock hardness, is the material coefficient of the hob.

[0017] As the preferred solution for the cutterhead of a curved hard rock tunnel boring machine, the model for controlling the driving force required for the cutterhead when tunneling in the preset tunneling mode is:

[0018] The excavation modes include hard rock excavation mode, soft rock excavation mode, earth pressure balance mode and slurry balance mode; Where, is the required driving force, is the cutter head diameter, is the digging resistance in the corresponding mode, The excavation mode coefficient of the corresponding mode is, They correspond to hard rock, soft rock, earth pressure balance and mud-water balance modes respectively.

[0019] The beneficial effects of the present invention are as follows: First, efficient and precise excavation: The curved design of the cutterhead panel perfectly matches the concave surface of the T-junction tunnel, greatly improving excavation efficiency and effectively solving the cutting difficulties of traditional cutterheads. The rock-breaking mechanism of the roller cutter, combined with the rational arrangement of the blades, ensures that adjacent blades penetrate the soil synchronously, resulting in more efficient rock crushing, reduced excavation time, and improved construction progress.

[0020] Second, the cutter is easy to replace: the cutter adopts a rear-mounted design. When the T-junction tunnel excavation distance is long and the cutter wears out, the cutter can be replaced easily without complicated procedures, ensuring the continuous and stable operation of the cutterhead, reducing equipment loss and construction costs.

[0021] Third, the mode is widely adaptable: it is not only suitable for open tunneling, but also can operate in earth pressure balance mode and slurry balance mode through structural adjustment, which enhances the adaptability of the cutterhead to different geological conditions and construction environments, expands the application range of the equipment, and provides strong support for various types of tunnel construction.

[0022] Fourth, the slag discharge system is optimized: the peripheral scrapers and scraper plates work together to scrape the slag into the slag collection device smoothly. The efficient slag discharge system avoids the impact of slag accumulation on the operation of the cutter head, ensures the stable operation of the cutter head, and further improves construction efficiency and equipment service life.

[0023] Fifth, tunneling performance improvement: By establishing a mathematical model of the cutter rock breaking efficiency, slag discharge efficiency, cutter wear degree and required driving force, a scientific basis is provided for the optimized design of the cutterhead and the adjustment of construction parameters, achieving precise control and further improving tunneling performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for the embodiments or the description of the prior art. Obviously, the drawings described below are merely exemplary, and those skilled in the art can, without inventive effort, derive other implementation drawings based on the provided drawings.

[0025] The structures, proportions, sizes, etc. illustrated in this specification are intended solely to complement the contents disclosed herein and to facilitate understanding and reading by persons skilled in the art. They are not intended to limit the conditions under which the present invention may be implemented and therefore have no substantive technical significance. Any structural modifications, changes in proportions, or adjustments in sizes, without affecting the efficacy and objectives of the present invention, shall remain within the scope of the technical contents disclosed herein.

[0026] Figure 1 A schematic diagram of the planar structure of a curved hard rock tunnel boring machine cutterhead provided in an embodiment of the present invention; Figure 2 A schematic cross-sectional structure diagram of a curved hard rock tunnel boring machine cutterhead provided in an embodiment of the present invention; Figure 3 A schematic diagram of a partial structure of a curved hard rock tunnel boring machine cutterhead provided in an embodiment of the present invention; Figure 4 This is a structural view of the excavation state of the starting cutterhead provided in an embodiment of the present invention; Figure 5 This is a schematic cross-sectional view of the curved cutter head with a twisted leg structure provided in an embodiment of the present invention.

[0027] In the figure: 1. Cutterhead structure; 1-1. Cutterhead panel; 1-2. Large ring; 1-3. Connecting ring; 1-4. Flange; 1-5. Scraper plate; 1-6. Twisted leg structure; 2. Hob; 3. Scraper; 4. Hob box. DETAILED DESCRIPTION

[0028] The following describes the implementation of the present invention using specific embodiments. Those skilled in the art will readily understand the other advantages and benefits of the present invention from the disclosure herein. Obviously, the embodiments described are only a portion of the present invention, not all of it. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without inventive effort are intended to fall within the scope of protection of the present invention.

[0029] See also Figure 1 、 Figure 2 、 Figure 3 and Figure 4 The embodiment of the present invention provides a curved hard rock tunnel boring machine cutter head, comprising: The cutterhead structure 1 includes a cutterhead panel 1-1, a large ring 1-2, a connecting ring 1-3, a flange 1-4, and a scraper 1-5. The cutterhead panel 1-1 has an arc-shaped cross-section and is used to fit the concave arc surface of the T-junction tunnel. The hob 2 is mounted on a hob box 4, the hob box 4 is fixed on the cutter head panel 1-1, and the blade of the hob 2 is arranged in an arc shape on the cutter head panel 1-1; The scraper 3 is arranged around the blade disc panel 1-1 and on the side of the connecting ring 1-3.

[0030] Specifically, the cutterhead panel 1-1 is designed with an arc-shaped structure because the concave surface of a T-junction tunnel is uniquely shaped. This curved structure allows it to better conform to the tunnel wall, reducing blind spots and improving excavation accuracy and efficiency. The large ring 1-2, connecting ring 1-3, and flange 1-4 work together to provide support and connection, ensuring the stability of the cutterhead structure 1 during rotation. The scraper 1-5 collects and removes debris during excavation. The cutterhead 2 is mounted on the cutterhead housing 4, which is fixed to the cutterhead panel 1-1, ensuring stable operation. The cutterhead 2's blades are curved, matching the curved shape of the cutterhead panel 1-1, ensuring more uniform rock crushing during rotation. Scrapers 3 are positioned around the cutterhead panel 1-1 and on the sides of the connecting ring 1-3. Their function is to scrape debris accumulated at the bottom of the cutterhead during rotation for subsequent removal.

[0031] In this embodiment, the cutter head panel 1-1 is connected to the large ring 1-2, the large ring 1-2 is connected to the flange 1-4 through the connecting ring 1-3, and the rear end of the flange 1-4 is connected to the intermediate drive or the peripheral drive.

[0032] Specifically, the cutterhead panel 1-1 is connected to the large circular ring 1-2, providing a basic support framework for the cutterhead. Large circular ring 1-2 is connected to flange 1-4 via connecting ring 1-3. This connection not only ensures a secure connection between the various parts of the cutterhead, but also disperses stress during torque transmission, preventing localized stress concentration. The rear end of flange 1-4 is connected to an intermediate drive or peripheral drive, effectively transmitting power from the drive unit to the cutterhead, driving its rotation. Different drive modes (intermediate drive or peripheral drive) can be selected based on actual construction requirements and equipment configuration to meet diverse working conditions.

[0033] In this embodiment, when the tunnel boring machine starts, the blades of the adjacent rollers 2 penetrate the soil synchronously, and the flanges 1-4 are driven to rotate by the rear drive. The rotational force is transmitted to the front roller 2 to rotate the roller 2, thereby achieving rock crushing and completing the excavation of the face.

[0034] Specifically, when the tunnel boring machine starts working, the blades of adjacent rollers 2 cut into the soil at the same time. This is based on the rock-breaking mechanism of the roller 2. The rear drive device drives the flange 1-4 to rotate. Since the roller cutter box 4 is fixed on the cutter head panel 1-1, and the cutter head panel 1-1 is connected to the flange 1-4 and other components, the rotational force of the flange 1-4 can be transmitted to the cutter head panel 1-1 and the roller cutter box 4 in turn, ultimately causing the roller 2 to rotate. During the rotation of the roller 2, the blade continuously squeezes and crushes the rock, peeling the rock off the face, thereby completing the excavation of the face. This method of synchronous penetration and rotational rock breaking can improve rock breaking efficiency and ensure the flatness of the excavation surface.

[0035] In this embodiment, after excavation is completed, the slag is accumulated at the bottom of the cutter disc, and the scraper 3 around it scrapes the slag into the scraper plate 1-5; when the cutter disc rotates, the scraper plate 1-5 drives the slag to rise, and after the slag reaches the set angle, it slides down through the scraper plate 1-5 and enters the belt conveyor slag collection device.

[0036] Specifically, during the excavation process, slag will accumulate at the bottom of the cutter disc. As the cutter disc rotates, the scrapers 3 around the cutter disc use their shape and position to scrape the slag toward the scraper plates 1-5. The scraper plates 1-5 rotate with the cutter disc. When the slag is scraped onto the scraper plates 1-5, the rotation of the scraper plates 1-5 drives the slag upward. When the slag rises to a certain angle, gravity overcomes the friction between the slag and the scraper plates 1-5, and the slag slides down the scraper plates 1-5 and into the belt conveyor slag collection device, thereby achieving the discharge of the slag. This slag discharge method utilizes the rotational motion of the cutter disc, does not require an additional power device, and has a simple structure and is highly efficient.

[0037] In this embodiment, when the excavation length of the T-junction tunnel reaches a set value, causing the wear degree of the roller cutter 2 and the scraper 3 to exceed the preset tool effective use threshold range, the roller cutter 2 is replaced.

[0038] Specifically, during the excavation of the T-tunnel, the cutter 2 and scraper 3 will constantly come into contact with rocks and slag, resulting in wear. As the excavation length increases, the degree of wear of the cutter will gradually increase. When the excavation length reaches the set value, the wear of the cutter may affect the excavation efficiency and the normal operation of the cutterhead. The preset effective use threshold range of the cutter is determined based on the material, design and actual construction experience of the cutter. When the tool wear exceeds this range, the rock-breaking ability of the cutter 2 will decrease, and the scraping effect of the scraper 3 will also deteriorate. At this time, in order to ensure the normal operation of the cutterhead, the cutter 2 needs to be replaced to ensure the smooth progress of the construction.

[0039] See also Figure 5 In a possible embodiment, it also includes a twisted leg structure 1-6. When the connecting ring 1-3 in the cutter head structure 1 is replaced by the twisted leg structure 1-6 and the scraper plate 1-5 is removed, it is applied to the earth pressure balance mode or the mud water balance mode.

[0040] Specifically, the twisted leg structure 1-6 is designed to adapt to the earth pressure balance mode and the slurry balance mode. In these two modes, the construction environment and requirements are different from those of open excavation. Replacing the connecting ring 1-3 with the twisted leg structure 1-6 can change the structural force mode of the cutterhead and better adapt to the effects of earth pressure or slurry pressure. The scraper plate 1-5 is removed because in the earth pressure balance or slurry balance mode, the discharge method of slag is different from the open type and no longer relies on the scraper plate 1-5 for slag discharge. The twisted leg structure 1-6 can enhance the stability and adaptability of the cutterhead in these special modes, ensuring that the cutterhead can work normally under different construction conditions.

[0041] In a possible embodiment, the rock breaking efficiency of the roller cutter 2 is related to the number of blades of the roller cutter 2, the blade shape, and the rotation speed of the roller cutter 2. The calculation formula of the rock breaking efficiency of the roller cutter 2 is:

[0042] Where, The rock breaking efficiency of disc cutter 2 is is the number of blades, is the blade shape coefficient, is the rotation speed of hob 2.

[0043] Specifically, the number of blades The more the blade shape coefficient is, the more times the disc cutter 2 contacts the rock in the same time, and the more rock is crushed, thus improving the rock breaking efficiency. This reflects the effect of blade shape on rock breaking efficiency. Different blade shapes have different mechanical properties when breaking rocks. For example, a sharp blade is easier to cut into rock, while a wider blade can better disperse the force when breaking rock. The faster the disc, the more times the disc cutter 2 impacts the rock per unit time, and the higher the rock-breaking efficiency. This formula comprehensively considers these three factors and can quantitatively describe the rock-breaking efficiency of disc cutter 2, providing a basis for cutterhead design and construction parameter adjustment.

[0044] In a possible embodiment, during the excavation process of the cutterhead, the slag discharge efficiency is related to the inclination angle of the scraper blades 1-5, the rotation speed of the cutterhead, and the amount of slag accumulation. The calculation formula for the slag discharge efficiency is: ( ) Where, For the slag discharge efficiency, is the inclination angle of the scraper plates 1-5, is the cutter head rotation speed, The amount of slag accumulation.

[0045] Specifically, the scraper blade has an inclination angle of 1-5 Determines the movement trend of the slag on the scraper 1-5. When the scraper 1-5 is tilted at a larger angle, the slag is more likely to slide down along the scraper 1-5 under the action of gravity, thereby improving the discharge efficiency. Here, the sine function is used to calculate the movement trend of the slag on the scraper 1-5. To reflect the influence of the inclination angle on the discharge efficiency. The faster the scraper blades 1-5 move, the faster the scraper blades 1-5 can move the scraper, which can bring the scraper to a higher position faster, increase the power of the scraper discharge, and thus improve the discharge efficiency. The larger the value, the more difficult it is to remove the slag under the same scraping and slag removal conditions, so the value of As the denominator, Increase in discharge efficiency It will decrease, reflecting the impact of slag accumulation on discharge efficiency.

[0046] In a possible embodiment, the degree of wear of the roller cutter 2 is related to the excavation distance, the rock hardness, and the material of the roller cutter 2. The calculation formula for the degree of wear of the roller cutter 2 is:

[0047] Where, is the wear degree of hob 2, is the excavation distance, is the rock hardness, is the material coefficient of hob 2.

[0048] Specifically, the excavation distance The longer the length, the more friction and collisions the disc cutter 2 will have with the rock, and the more severe the wear will be. It is one of the key factors affecting the wear of the cutter 2. The higher the hardness of the rock, the stronger the wear on the cutter 2. It reflects the wear resistance of the hob 2 material. Hobs 2 made of different materials have different wear resistance. A larger value indicates a lower wear resistance for the cutter material, and at the same excavation distance and rock hardness, the wear increases. This formula quantifies the wear of cutter 2 using these three factors, helping construction personnel predict cutter wear in advance and implement timely tool replacement and maintenance.

[0049] In a possible embodiment, when the cutterhead is driving in a preset driving mode, the model of the driving force required to control the cutterhead is:

[0050] The excavation modes include hard rock excavation mode, soft rock excavation mode, earth pressure balance mode and mud-water balance mode; where, is the required driving force, is the cutter head diameter, is the digging resistance in the corresponding mode, is the excavation mode coefficient of the corresponding mode, They correspond to hard rock, soft rock, earth pressure balance and mud-water balance modes respectively.

[0051] The driving force required when the cutterhead is engaged in different excavation modes is related to the cutterhead diameter, excavation resistance, and excavation mode coefficient. The excavation modes include but are not limited to hard rock excavation mode, soft rock excavation mode, earth pressure balance mode, and slurry balance mode.

[0052] When in hard rock excavation mode, the rock hardness is high and it is difficult for the cutter head to break the rock. The excavation resistance mainly comes from the reaction force of the rock on the disc cutter 2 and scraper 3. At this time, the excavation mode coefficient is , assuming the required driving force is , the cutter head diameter is , the excavation resistance is , satisfying the mathematical model formula: .

[0053] When in soft rock excavation mode, the rock hardness is relatively low, the cutter head breaks the rock relatively easily, and the excavation resistance is reduced compared to the hard rock mode. At this time, the excavation mode coefficient is ( ), assuming the required driving force is , the excavation resistance is ( ), satisfying the mathematical model formula: .

[0054] When in earth pressure balance mode, the connecting ring 1-3 in the cutterhead structure 1 is replaced by the twisted leg structure 1-6 and the scraper 1-5 is removed. The excavation resistance mainly includes the friction and extrusion resistance of the soil on the cutterhead. At the same time, the pressure balance in the soil bin needs to be maintained. At this time, the excavation mode coefficient is , assuming the required driving force is , the excavation resistance is , satisfying the mathematical model formula: .

[0055] When in mud-water balance mode, the cutterhead structure 1 is also adjusted accordingly. The excavation resistance is mainly the resistance of mud-water to the cutterhead and the resistance to be overcome to maintain the mud-water pressure balance. At this time, the excavation mode coefficient is , assuming the required driving force is , the excavation resistance is , satisfying the mathematical model formula: .

[0056] Specifically, the cutter head diameter The larger the diameter, the greater the inertia and friction that must be overcome during rotation, and the greater the driving force required. It is closely related to different excavation modes. In hard rock excavation mode, the rock hardness is high and the excavation resistance is large; in soft rock excavation mode, the excavation resistance is relatively small; in earth pressure balance mode and slurry balance mode, the excavation resistance is affected by factors such as soil pressure and slurry pressure. Excavation mode coefficient This model is designed to account for differences in cutterhead operating characteristics and efficiency under different tunneling modes. For example, in hard rock tunneling, due to the greater difficulty in breaking rock, a higher driving force coefficient is required to ensure the cutterhead operates properly; in soft rock tunneling, the driving force coefficient is relatively small. This model accurately calculates the required driving force based on different tunneling modes and cutterhead parameters, providing a reference for the selection and design of the drive unit.

[0057] The workflow of the present invention is as follows: First, cutterhead assembly and connection Before construction, the cutterhead structure 1 is assembled first, and the cutterhead panel 1-1, large ring 1-2, connecting ring 1-3, and flange 1-4 are connected in sequence. Among them, the cross-section of the cutterhead panel 1-1 is an arc-shaped structure, which can perfectly fit the concave arc surface of the T-junction tunnel. The hob 2 is installed on the hob cutter box 4, and then the hob cutter box 4 is fixed to the cutterhead panel 1-1, so that the blade of the hob 2 is arranged in an arc shape on the cutterhead panel 1-1. At the same time, the scraper 3 is arranged around the cutterhead panel 1-1 and on the side of the connecting ring 1-3. Finally, the rear end of the flange 1-4 is connected to the intermediate drive or peripheral drive device to allow power to be transmitted to the cutterhead.

[0058] Second, the start of the tunnel boring machine and rock breaking When the tunnel boring machine begins operation, the blades of adjacent cutters 2 penetrate the soil simultaneously. The rear drive unit drives the flange 1-4 to rotate. Since the cutter box 4 is connected to the cutterhead panel 1-1, the rotational force is transmitted to the front cutter 2, causing it to rotate. As the cutter 2 rotates, its blades continuously squeeze and crush the rock, stripping it from the tunnel face and completing the excavation of the tunnel face. The rock breaking efficiency of cutter 2 is related to the number of blades, blade shape, and the rotation speed of cutter 2, which can be calculated by the formula Calculate, where The rock breaking efficiency of disc cutter 2 is is the number of blades, is the blade shape coefficient, is the rotation speed of hob 2.

[0059] Third, slag discharge After excavation is completed, the slag will accumulate at the bottom of the cutter disc. The scrapers 3 around the cutter disc rotate with the cutter disc, scraping the slag into the scraper plates 1-5. The scraper plates 1-5 drive the slag upward as the cutter disc rotates. When the slag reaches the set angle, gravity overcomes the friction between the slag and the scraper plates 1-5, and the slag will slide down the scraper plates 1-5 and enter the belt conveyor slag collection device. The slag discharge efficiency is related to the inclination angle of the scraper plates 1-5, the rotation speed of the cutter disc, and the amount of slag accumulation. It can be calculated by the formula ( ) calculation, where For the slag discharge efficiency, The scraper blade has an inclination angle of 1-5. is the cutter head rotation speed, The amount of slag accumulation.

[0060] Fourth, tool replacement During the excavation of the T-junction tunnel, the cutter 2 and scraper 3 will wear out due to continuous contact with rocks and slag. When the excavation length of the T-junction tunnel reaches the set value and the wear degree of the cutter 2 and scraper 3 exceeds the preset tool effective use threshold range, the cutter 2 needs to be replaced to ensure the normal operation of the cutterhead. The wear degree of the cutter 2 is related to the excavation distance, rock hardness and the material of the cutter 2. The formula Calculate, where is the wear degree of hob 2, is the excavation distance, is the rock hardness, is the material coefficient of hob 2.

[0061] Fifth, mode switching To use the cutterhead in earth pressure balance or slurry balance mode, the connecting ring 1-3 in the cutterhead structure 1 must be replaced with a twisted leg structure 1-6, and the scraper blade 1-5 must be removed. The twisted leg structure 1-6 changes the way the cutterhead is subjected to force, allowing it to better adapt to earth pressure or slurry pressure, meeting the needs of different construction modes.

[0062] Sixth, driving force control The driving force required by the cutterhead is different when it is excavating in different excavation modes (hard rock, soft rock, earth pressure balance, and mud water balance). The model for controlling the driving force required by the cutterhead is: ( Corresponding to hard rock, soft rock, earth pressure balance, and mud water balance modes respectively), is the required driving force, is the cutter head diameter, is the digging resistance in the corresponding mode, is the tunneling mode coefficient for the corresponding mode. During construction, the required driving force can be accurately calculated based on the specific mode and cutterhead parameters, providing a basis for the selection and design of the drive device.

[0063] Although the present invention has been described in detail above using general descriptions and specific embodiments, it will be apparent to those skilled in the art that modifications and improvements may be made thereto. Therefore, such modifications and improvements, without departing from the spirit of the present invention, are intended to be within the scope of protection claimed herein.

Claims

1. A curved hard rock tunnel boring machine cutterhead, characterized in that: include: A cutterhead structure (1) comprises a cutterhead panel (1-1), a large circular ring (1-2), a connecting ring (1-3), a flange (1-4), and a scraper plate (1-5); the cutterhead panel (1-1) has an arc-shaped cross-section and is used to fit the concave arc surface of a T-junction tunnel; A hob (2) is mounted on a hob box (4), the hob box (4) is fixed on the cutter head panel (1-1), and the blade of the hob (2) is arranged in an arc shape on the cutter head panel (1-1); The scraper (3) is arranged around the periphery of the cutter head panel (1-1) and on the side of the connecting ring (1-3).

2. The arc-shaped hard rock tunnel boring machine cutter head according to claim 1, characterized in that: The cutter head panel (1-1) is connected to the large circular ring (1-2), the large circular ring (1-2) is connected to the flange (1-4) via the connecting ring (1-3), and the rear end of the flange (1-4) is connected to an intermediate drive or a peripheral drive.

3. The arc-shaped hard rock tunnel boring machine cutter head according to claim 1, characterized in that: When the tunnel boring machine starts, the blades of the adjacent roller cutters (2) penetrate the soil synchronously, and the flanges (1-4) are driven to rotate by the rear drive, and the rotational force is transmitted to the front roller cutter (2) to rotate the roller cutter (2), thereby achieving rock crushing and completing the excavation of the tunnel face.

4. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: After excavation is completed, the slag is accumulated at the bottom of the cutter head, and the scrapers (3) around it scrape the slag into the scraper plates (1-5); When the cutter disc rotates, the scraper plate (1-5) drives the slag to rise, and after the slag reaches a set angle, it slides down through the scraper plate (1-5) and enters the belt conveyor slag collecting device.

5. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: When the excavation length of the T-junction tunnel reaches a set value, causing the wear degree of the roller cutter (2) and the scraper (3) to exceed a preset effective tool use threshold range, the roller cutter (2) is replaced.

6. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: It also includes a twisted leg structure (1-6). When the connecting ring (1-3) in the cutter head structure (1) is replaced with the twisted leg structure (1-6) and the scraper plate (1-5) is removed, it is applied to an earth pressure balance mode or a mud-water balance mode.

7. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: The rock breaking efficiency of the roller cutter (2) is related to the number of blades of the roller cutter (2), the blade shape and the rotation speed of the roller cutter (2). The calculation formula of the rock breaking efficiency of the roller cutter is: ； Where, For the rock breaking efficiency of the roller cutter, The number of blades is, is the blade shape coefficient, is the reel rotation speed.

8. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: During the excavation process of the cutterhead, the slag discharge efficiency is related to the inclination angle of the scraper blade (1-5), the rotation speed of the cutterhead and the accumulation of slag. The calculation formula of the slag discharge efficiency is: ； Where, For the slag discharge efficiency, is the inclination angle of the scraper (1-5), is the cutter head rotation speed, The amount of slag accumulation.

9. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: The degree of wear of the roller cutter (2) is related to the excavation distance, the hardness of the rock and the material of the roller cutter (2). The calculation formula for the degree of wear of the roller cutter is: ； Where, is the degree of wear of the hob, is the excavation distance, is the rock hardness, is the material coefficient of the hob.

10. The arc-shaped hard rock tunnel boring machine cutterhead according to claim 1, characterized in that: When the cutterhead is driving in the preset excavation mode, the model of the driving force required to control the cutterhead is: ； The excavation modes include hard rock excavation mode, soft rock excavation mode, earth pressure balance mode and slurry balance mode; Where, is the required driving force, is the cutter head diameter, is the digging resistance in the corresponding mode, The excavation mode coefficient of the corresponding mode is, They correspond to hard rock, soft rock, earth pressure balance and mud-water balance modes respectively.

Images