Methods, devices, equipment, and tunnel boring machines for predicting cutter wear.

Abstract

The application discloses a method, device and equipment for predicting cutter wear and a shield tunneling machine, and relates to the technical field of tunnel construction. The method for predicting cutter wear comprises the following steps: determining a first normal force borne by a cutter when rolling and crushing rocks by means of rock strength, penetration and geometric parameters of the cutter; determining a second normal force borne by the cutter when slidingly cutting soil layers by means of geometric parameters of the cutter, an internal friction angle, cohesive force, penetration and mechanical action between the cutter and the muck; determining a basic cutter wear model based on a sum of the first energy action of the cutter in the rock stratum and the second energy action of the cutter in the soil layer, cutter ring hardness and a wear coefficient; and predicting cumulative cutter wear according to the number of shield tunneling rings and the basic cutter wear model. By executing the above steps, the prediction accuracy of cutter wear can be improved.

Description

Technical Field

[0001] This application relates to the field of tunnel construction technology, and in particular to a method, device, equipment and tunnel boring machine for predicting cutter wear. Background Technology

[0002] Cutterhead wear is one of the most concerning issues in shield tunneling under complex geological conditions. Severe cutterhead wear, along with problems such as excavation face instability and uneven ground settlement caused by cutterhead replacement operations, significantly increases construction difficulty, delays the construction period, increases construction risks, and introduces numerous uncertainties to the surrounding environment.

[0003] Most predictions of hob wear in related technologies are based on homogeneous strata, which leads to a large error between the predicted hob wear and the actual hob wear. Summary of the Invention

[0004] The main objective of this application is to provide a method, apparatus, equipment, and tunnel boring machine for predicting cutter wear, aiming to improve the accuracy of cutter wear prediction.

[0005] To achieve the above objectives, one aspect of this application proposes a method for predicting cutter wear, comprising the following steps: determining the first positive force exerted by the cutter on rock crushing using rock strength, penetration depth, and cutter geometry; determining the second positive force exerted by the cutter on soil layer sliding using cutter geometry, internal friction angle, cohesion, penetration depth, and mechanical interaction between the cutter and the excavated soil; determining a basic cutter wear model based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient, wherein the first energy action is expressed as the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is expressed as the product of the second positive force and the sliding distance of the cutter in the soil layer; and predicting the cumulative wear of the cutter based on the shield tunneling ring number and the basic cutter wear model.

[0006] In some embodiments, the geometric parameters of the cutter include the cutter radius, the cutter blade width, and the cutter spacing; the rock strength includes the uniaxial compressive strength and the tensile strength of the rock; determining the first positive force on the rock being crushed by the cutter using the rock strength, penetration depth, and the geometric parameters of the cutter includes: determining the first positive force by the quotient of a first formula and the cutter blade width, wherein the first formula is determined by the product of the power of a first sub-formula, the power of the cutter radius, the power of the uniaxial compressive strength of the rock, and the power of the cutter blade width; and the first sub-formula is represented by the product of the cutter spacing, the penetration depth, and the tensile strength of the rock.

[0007] In some embodiments, the geometric parameters of the cutter include the cutter radius and the cutter ring angle; the mechanical interaction between the cutter and the excavated soil includes the contact pressure between the cutter and the excavated soil; determining the second positive force on the soil layer by the cutter sliding through the cutter's geometric parameters, internal friction angle, cohesion, penetration depth, and the mechanical interaction between the cutter and the excavated soil includes: determining the second positive force on the soil layer by the cutter sliding through a second formula; the second formula is expressed as:

[0008]

[0009] in, The second positive force is represented by μ, the sliding friction coefficient between the cutter and the rock is represented by r, the radius of the cutter is represented by p, the cutter penetration is represented by P, and the contact pressure between the cutter and the slag is represented by P. Let c0 be the internal friction angle, c0 be the cohesion, and α be the hob cutter ring cutting edge angle. In this context, 'n' represents the positive force. In this context, 's' represents sliding.

[0010] In some embodiments, determining the wear model of the foundation cutter based on the sum of the first energy action of the cutter in the rock stratum and the second energy action of the cutter in the soil stratum, the cutter ring hardness, and the wear coefficient includes: determining the wear model of the foundation cutter using a third formula; the third formula is expressed as:

[0011]

[0012] Where w is the basic hob wear amount, and k s H is the wear coefficient, and H is the hardness of the hob ring. For the first positive force, s h The sliding distance of the cutter in the rock strata. For the second positive force, s s The sliding distance of the cutter in the soil layer. In this context, 'n' represents the positive force. In this context, 'r' indicates scrolling.

[0013] In some embodiments, the method for predicting hob wear further includes determining the hardness of the hob ring. Determining the hardness of the hob ring includes: measuring the hardness at multiple different locations uniformly distributed circumferentially on the hob ring to obtain multiple initial hob ring hardnesses; determining the average value of the multiple initial hob ring hardnesses; and determining the average value as the hob ring hardness.

[0014] In some embodiments, predicting the cumulative wear of the cutter head based on the number of tunneling rings and the basic cutter head wear model includes: inputting parameters of any one ring of tunneling by the tunnel boring machine into the basic cutter head wear model to obtain the radial wear of the cutter head when tunneling any one ring, wherein the parameters correspond to the parameters in the basic cutter head wear model; and predicting the cumulative wear of the cutter head using a fourth formula; the fourth formula is expressed as:

[0015]

[0016] Among them, w m w represents the cumulative wear of the cutterhead after excavating m rings; m is the number of shield tunneling rings. i This represents the radial wear of the cutter head during the excavation of the i-th ring.

[0017] In some embodiments, the method for predicting cutter wear further includes: determining the sliding distance of the cutter in the rock and soil layers based on the penetration depth, cutter radius, cutter installation radius, advance distance of one ring of tunneling by the tunnel boring machine, tunnel excavation diameter, and height of the soil-rock interface.

[0018] To achieve the above objectives, another aspect of this application proposes a device for predicting cutter wear. The device includes: a first determining module for determining a first positive force exerted by the cutter on rock through rock strength, penetration depth, and the cutter's geometric parameters; a second determining module for determining a second positive force exerted by the cutter on soil through the cutter's geometric parameters, internal friction angle, cohesion, penetration depth, and the mechanical interaction between the cutter and the excavated soil; a third determining module for determining a basic cutter wear model based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient, wherein the first energy action is expressed as the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is expressed as the product of the second positive force and the sliding distance of the cutter in the soil layer; and a prediction module for predicting the cumulative wear of the cutter based on the number of shield tunneling rings and the basic cutter wear model.

[0019] To achieve the above objectives, another aspect of this application provides an electronic device, which includes a memory and a processor. The memory stores a computer program, and the processor executes the computer program to implement the above-described method for predicting hob wear.

[0020] To achieve the above objectives, another aspect of the embodiments of this application proposes a tunnel boring machine (TBM) in which the wear amount of the cutterheads in the TBM is predicted by the aforementioned cutterhead wear prediction device or the aforementioned electronic device.

[0021] The embodiments of this application include at least the following beneficial effects:

[0022] This application provides a method, apparatus, equipment, and tunnel boring machine for predicting cutter wear. In the embodiments of this application, firstly, the first positive force on the cutter rolling and breaking rock is determined by the rock strength, penetration depth, and cutter geometry parameters. Secondly, the second positive force on the cutter sliding and cutting soil is determined by the cutter geometry parameters, internal friction angle, cohesion, penetration depth, and mechanical interaction between the cutter and the excavated soil. Thirdly, a basic cutter wear model is determined based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient. The first energy action is expressed as the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is expressed as the product of the second positive force and the sliding distance of the cutter in the soil layer. Finally, the cumulative wear of the cutter is predicted based on the number of tunnel boring rings and the basic cutter wear model. The basic cutter wear model, determined by combining the first energy effect of the cutter in the rock strata and the second energy effect of the cutter in the soil strata, the cutter ring hardness, and the wear coefficient, fully considers the energy effect of the cutter in both rock and soil strata. The basic cutter wear model constructed by combining these two factors, along with the cumulative wear of the cutter predicted by the number of shield tunneling rings, shows a smaller error compared to related cutter wear prediction methods, thus improving the accuracy of cutter wear prediction.

[0023] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0024] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0025] Figure 1 This is a flowchart of a method for predicting hob wear provided in some embodiments of this application;

[0026] Figure 2 This is a coordinate graph showing the predicted hob wear amount provided in some embodiments of this application;

[0027] Figure 3 This is a schematic block diagram of a hob wear prediction device provided in some embodiments of this application;

[0028] Figure 4 These are schematic diagrams of the hardware structure of electronic devices provided in some embodiments of this application. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the reference to "embodiment" herein means that a specific feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it an independent or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments. The implementation methods described in the following exemplary embodiments do not represent all implementation methods consistent with the embodiments of this application; they are merely examples of apparatuses and methods consistent with some aspects of the embodiments of this application as detailed in the appended claims.

[0030] It is understood that the terms “first,” “second,” etc., used in this application may be used herein to describe various concepts, but unless otherwise stated, these concepts are not limited by these terms. These terms are only used to distinguish one concept from another. For example, without departing from the scope of the embodiments of this application, first information may also be referred to as second information, and similarly, second information may also be referred to as first information. Depending on the context, the words “if,” “when,” or “in response to a determination” as used herein may be interpreted as “when…”, “in the case of…”, or “in the circumstances of…”.

[0031] As used in this application, the terms "at least one", "multiple", "each", "any", etc., "at least one" includes one, two or more, "multiple" includes two or more, "each" refers to each of the corresponding multiples, and "any" refers to any one of the multiples.

[0032] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing embodiments of this application only and is not intended to limit this application.

[0033] In the following description, specific details such as particular system architectures and techniques are set forth for illustrative purposes and not for limitation, in order to provide a thorough understanding of the embodiments of this application. However, those skilled in the art will understand that this application may also be implemented in other embodiments without these specific details. In other instances, detailed descriptions of well-known systems, apparatuses, circuits, and methods have been omitted so as not to obscure the description of this application with unnecessary detail.

[0034] To facilitate understanding of the inventive concept of this application, before providing a detailed description of the embodiments of this application, the English abbreviations (terms) / related concepts involved in the embodiments of this application will be explained first. The English abbreviations (terms) / related concepts involved in the embodiments of this application are subject to the following interpretation.

[0035] Tunnel Boring Machine (TBM): A TBM is a mechanical device used for tunnel construction. Its working principle primarily involves a cylindrical steel assembly advancing along the tunnel axis while excavating the soil. The shell of this cylindrical assembly, the shield, provides temporary support for the excavated, unlined tunnel section, bearing the pressure of the surrounding soil layers and sometimes groundwater pressure, while also blocking groundwater from entering. TBMs can be classified into various types according to different criteria. For example, based on whether there is a stable excavation face, they are classified as closed-face, open, and semi-open types; based on the method of controlling excavation face stability, they are classified as slurry TBMs, earth pressure balance TBMs, combined TBMs, and compressed air TBMs, etc.

[0036] Shield tunneling is a fully mechanized construction method primarily used for underground tunnel construction. This method involves using a shield tunneling machine to advance through the ground, utilizing the shield's outer shell and tunnel segments to support the surrounding rock and prevent tunnel collapse.

[0037] Cutter wear is one of the most concerning issues in shield tunneling under complex geological conditions. Severe cutter wear and problems such as excavation face instability and uneven ground settlement caused by cutter replacement operations significantly increase construction difficulty, delays, and risks, while also introducing numerous uncertainties to the surrounding environment. Currently, there is a lack of scientifically reliable methods for predicting cutter wear under complex geological conditions. With the rapid development of subway tunnel construction in my country, research on the wear mechanism of cutters under complex geological conditions and the decision-making process for cutter replacement during shield tunneling have become particularly urgent.

[0038] Existing methods for predicting cutter wear primarily target homogeneous strata, lacking methods for predicting cutter wear in soil-rock interfacial strata. These methods assume that the cutters at different positions on the cutterhead uniformly distribute the shield thrust required for cutting the strata, allocating the torque needed for cutting to different cutter positions based on the installation radius of each cutter. However, when the tunnel boring machine (TBM) is excavating in soil-rock interfacial strata, the cutters alternately cut through soil and rock layers as the cutterhead rotates. Due to the significant differences in strength between different strata, existing methods fail to account for the substantial differences in cutting forces, leading to significant errors in the predicted cutter wear.

[0039] In view of this, this application proposes a method, device, equipment, and tunnel boring machine for predicting cutter wear. The scheme first determines the first positive force exerted by the cutter on the rock through rock strength, penetration depth, and cutter geometry. Then, it determines the second positive force exerted by the cutter on the soil through cutter geometry, internal friction angle, cohesion, penetration depth, and the mechanical interaction between the cutter and the excavated soil. Next, based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient, a basic cutter wear model is determined. The first energy action is expressed as the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is expressed as the product of the second positive force and the sliding distance of the cutter in the soil layer. Finally, the cumulative wear of the cutter is predicted based on the number of tunnel boring rings and the basic cutter wear model. The basic cutter wear model, determined by combining the first energy effect of the cutter in the rock strata and the second energy effect of the cutter in the soil strata, the cutter ring hardness, and the wear coefficient, fully considers the energy effect of the cutter in both rock and soil strata. The basic cutter wear model constructed by combining these two factors, along with the cumulative wear of the cutter predicted by the number of shield tunneling rings, shows a smaller error compared to related cutter wear prediction methods, thus improving the accuracy of cutter wear prediction.

[0040] The method provided in this application embodiment can be applied to the tunnel boring machine and / or electronic equipment provided in this application embodiment, wherein the electronic equipment can be a terminal or a server.

[0041] The terminal can be a tablet computer, a laptop computer, a desktop computer, etc., but is not limited to these.

[0042] A server can be a standalone physical server, a server cluster or distributed system consisting of multiple physical servers, or a cloud server that provides basic cloud computing services such as cloud services, cloud databases, cloud computing, cloud functions, cloud storage, network services, cloud communication, middleware services, domain name services, security services, content delivery networks, and big data and artificial intelligence platforms.

[0043] The implementation steps of a hob wear prediction method provided in this application embodiment will be described in detail below with reference to the accompanying drawings.

[0044] Please refer to Figure 1 , Figure 1 The flowchart illustrates a method for predicting hob wear in some embodiments of this application. It should be noted that the steps shown in the flowchart can be executed in a computer system such as a set of computer-executable instructions, and although a logical order is shown in the flowchart, in some cases the steps shown or described may be executed in a different order than that shown here.

[0045] The method of the embodiments of this application includes the following steps:

[0046] Step 101: Determine the first positive force on the rock being broken by the roller cutter by considering the rock strength, penetration depth, and the geometric parameters of the roller cutter;

[0047] Step 102: Determine the second positive force on the soil layer when the cutter slides and cuts through the geometric parameters, internal friction angle, cohesion, penetration, and mechanical interaction between the cutter and the slag.

[0048] Step 103: Based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness and wear coefficient, determine the wear amount model of the basic cutter. The first energy action is represented by the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is represented by the product of the second positive force and the sliding distance of the cutter in the soil layer.

[0049] Step 104: Predict the cumulative wear of the cutterheads based on the model of the number of tunneling rings and the wear of the cutterheads in the foundation.

[0050] Steps 101 to 104 of the embodiments of this application, through the sum of the first energy action of the cutter in the rock stratum and the second energy action of the cutter in the soil stratum, the cutter ring hardness and the wear coefficient, determine the basic cutter wear model, which fully considers the energy action of the cutter in the rock stratum and the soil stratum. By combining the basic cutter wear model constructed by the two and the cumulative wear of the cutter predicted by the number of shield tunneling rings, compared with the relevant cutter wear prediction methods, the error between it and the actual wear of the cutter is smaller, thereby improving the accuracy of the cutter wear prediction.

[0051] Before performing the above steps, the motion pattern of the cutterhead cutting the soil layer can be determined. It should be understood that the motion pattern of the cutterhead cutting the soil layer often differs depending on different geological conditions. Under certain conditions, the cutterhead can switch from one motion pattern to another.

[0052] For example, when the condition shown in equation (1) is met, the cutter will cut the soil layer in a sliding manner.

[0053]

[0054] Where, σ c S is the rock compressive strength, p is the cutter penetration, r is the cutter radius, α is the cutter ring angle, μ is the sliding friction coefficient between the cutter and the rock, P is the contact pressure between the cutter and the slag, and its magnitude is equal to the water and soil pressure at the working face. r S is the contact area between the cutter head and the excavated soil.b R is the contact area between the cutter body and the slag. r R is the average distance from the hob cutter ring to the geometric center of the hob. b T0 is the average distance from the hob body to the geometric center of the hob, and T0 is the hob starting torque.

[0055] The specific implementation methods for each of the above steps are described below.

[0056] In step 101, the first positive force on the rock being broken by the rolling cutter is determined by the rock strength, penetration depth and the geometric parameters of the cutter.

[0057] Rock strength generally refers to the ability of a rock to resist external forces without breaking. Rock strength includes compressive strength and tensile strength. Compressive strength is the maximum pressure a rock can withstand under uniaxial compression conditions, typically determined through compression tests on cubic or cylindrical specimens. Tensile strength is the ability of a rock to resist tensile failure, usually determined through direct tensile tests or the Brazilian disc test.

[0058] Penetration refers to the depth to which the cutter cuts into the rock during its advance. It reflects the rock-breaking ability of the cutter under a certain thrust and rotation speed. Specifically, it can refer to the average depth to which the cutter cuts into the rock per revolution.

[0059] The geometric parameters of a cutting cutter typically refer to its size and shape characteristics, including the cutter radius, cutting edge width, and cutter spacing. It should be understood that rocks of different hardness and structure may require cutting cutters with different geometric parameters, and these parameters will affect the cutter's penetration depth and excavation efficiency, as well as its wear resistance and service life.

[0060] Roller crushing of rock utilizes rollers to apply pressure to the rock surface, causing the rock to fracture through compression and shearing. The initial normal force acting on the rock during roller crushing can typically be determined by the rock strength, penetration depth, and the geometric parameters of the rollers. Alternatively, it can be calculated using the rock's compressive strength, the contact area between the rollers and the rock, and the roller pressure. It can also be determined using existing models and empirical formulas; this application does not impose any limitations on these methods.

[0061] In some embodiments of this application, the geometric parameters of the cutter include the cutter radius, the cutter blade width, and the cutter spacing, and the rock strength includes the uniaxial compressive strength and the tensile strength of the rock. The first positive force can be determined by the quotient of a first formula and the cutter blade width, wherein the first formula is determined by the product of the powers of a first sub-formula, the power of the cutter radius, the power of the uniaxial compressive strength of the rock, and the power of the cutter blade width, and the first sub-formula is expressed as the product of the cutter spacing, penetration depth, and the tensile strength of the rock.

[0062] For example, the first positive force on the rock being crushed by the cutter can be calculated using formula (2), which can be expressed as:

[0063]

[0064] in, σ is the normal force exerted by the roller cutter on the rock; C is a constant, which can take a value of 2.12; r is the radius of the roller cutter; T is the width of the roller cutter blade; S is the distance between the cutters; σ c σ is the uniaxial compressive strength of the rock. t The tensile strength of the rock can be taken as 1 / 15 of the compressive strength of the rock. The contact angle between the blade ring and the rock.

[0065] The embodiments of this application determine the first positive force on the rock crusher by the rock strength, penetration and the geometric parameters of the cutter, which improves the calculation accuracy of the positive force on the rock crusher and provides support for predicting the wear of the cutter.

[0066] In step 102, the second positive force on the soil layer during the sliding cutter cutting can be determined by the cutter's geometric parameters, internal friction angle, cohesion, penetration, and the mechanical interaction between the cutter and the soil.

[0067] The mechanical interaction between the cutterhead and the excavated soil typically refers to the interaction forces and influences between the cutterhead and the excavated soil during the tunneling process of a tunnel boring machine (TBM). This mechanical interaction includes the contact pressure between the cutterhead and the excavated soil.

[0068] The second positive force experienced by the roller cutter during sliding cuts of the soil layer can be determined by the geometric parameters of the roller cutter, the internal friction angle, the cohesion, the penetration depth, and the mechanical interaction between the roller cutter and the soil. It can also be determined by the product of the contact area between the roller cutter and the soil layer and the effective stress of the soil layer. Alternatively, it can be estimated by combining empirical formulas with historical data. This application does not impose any restrictions on this.

[0069] In some embodiments of this application, the geometric parameters of the cutter include the cutter radius and the cutter ring cutting angle, and the mechanical interaction between the cutter and the soil includes the contact pressure between the cutter and the soil. For example, the second positive force on the cutter sliding and cutting the soil layer can be determined by formula (3).

[0070] Equation (3) is expressed as:

[0071]

[0072] in, The second positive force is represented by μ, the coefficient of sliding friction between the cutter and the rock is represented by r, the radius of the cutter is represented by p, the cutter penetration is represented by P, and the contact pressure between the cutter and the slag is represented by P. Let c0 be the internal friction angle, c0 be the cohesion, and α be the hob cutter ring cutting edge angle. In this context, 'n' represents the positive force. In this context, 's' represents sliding.

[0073] The embodiments provided in this application determine the second positive force experienced by the roller cutter during sliding cuts of the soil layer by using the roller cutter's geometric parameters, internal friction angle, cohesion, penetration, and the mechanical interaction between the roller cutter and the slag. This allows for accurate estimation of the positive force experienced by the roller cutter during sliding cuts of the soil layer, providing support for predicting the amount of roller cutter wear.

[0074] In step 103, the wear model of the basic cutter is determined based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient. The first energy action is represented as the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is represented as the product of the second positive force and the sliding distance of the cutter in the soil layer.

[0075] In some implementations, the basic hob wear model can be represented by formula (4).

[0076]

[0077] Where w is the basic hob wear amount, and k s H is the wear coefficient, and H is the hardness of the hob ring. For the first positive force, s h This represents the sliding distance of the cutting tool in the rock strata. For the second positive force, s s This represents the sliding distance of the cutting tool in the soil layer. In this context, 'n' represents the positive force. In this context, 'r' indicates rolling.

[0078] In some implementations, the hardness of the hob cutter ring can be determined by measuring the hardness at multiple different locations uniformly distributed around the hob cutter ring to obtain multiple initial cutter ring hardnesses, determining the average value of the multiple initial cutter ring hardnesses, and defining the average value as the hob cutter ring hardness.

[0079] Optionally, the hardness of the hob ring can be measured using a portable hardness tester. During measurement, five different locations evenly distributed around the circumference of each hob ring can be selected for hardness measurement, and the average of the five measurement results is taken as the final measurement result.

[0080] For example, for a No. 35 hob, the hardness of five different positions of the hob ring evenly distributed in the circumference is measured by a hardness tester, and the hardnesses are 54, 52, 53, 54 and 52 respectively. Then the hardness of the hob ring of No. 35 can be determined as (54+52+53+54+52) / 5=53.

[0081] In some implementations, the sliding distance of the cutter in the rock and soil layers can also be determined based on the penetration depth, cutter radius, cutter installation radius, the forward distance of one ring of tunneling by the tunnel boring machine, the tunnel excavation diameter, and the height of the soil-rock interface.

[0082] Alternatively, the sliding distance of the cutter in the soil layer can be calculated using formula (5).

[0083]

[0084] Among them, s s denoted as ρ, where p is the sliding distance of the cutterhead in the soil layer, R is the installation radius of the cutterhead, L is the forward distance of one ring excavation by the tunnel boring machine, D is the diameter of the tunnel boring machine, and x is the height of the soil-rock interface.

[0085] It should be understood that the hob radius usually refers to the radius of the hob's cutting edge, that is, the distance from the center line of the cutting edge to the outermost edge. The hob's mounting radius refers to the distance from the hob's mounting position on the cutter head to the cutter head's axis of rotation.

[0086] The shield excavation diameter refers to the maximum diameter that the cutterhead at the front end of the tunnel boring machine (TBM) can cut and pass through during tunnel excavation. This diameter determines the maximum diameter of the tunnel that the TBM can excavate.

[0087] The distance a tunnel boring machine (TBM) travels in one ring typically refers to the length of tunnel it needs to complete one full advance and install one ring of tunnel lining (such as segments). The length of one ring is usually equal to the width of the tunnel lining.

[0088] Alternatively, the sliding distance of the cutter in the rock strata can be calculated using formula (6).

[0089]

[0090] Among them, s h denoted as ρ, where p is the sliding distance of the cutterhead in the rock stratum; ρ is the penetration depth; R is the installation radius of the cutterhead; L is the forward distance of one ring excavation by the tunnel boring machine; D is the tunnel boring machine excavation diameter; x is the height of the soil-rock interface; μ represents the sliding friction coefficient between the cutterhead and the rock; and r represents the radius of the cutterhead.

[0091] To facilitate the calculation of the sliding distance of the cutterhead in rock and soil layers, the length s of the cutterhead's trajectory during the excavation of one ring of the tunnel boring machine can be calculated first. t .

[0092] The length of the cutterhead movement trajectory of the tunnel boring machine can be calculated using formula (7).

[0093]

[0094] Where L is the distance the tunnel boring machine travels in one ring, p is the penetration depth, and R is the installation radius of the cutter head.

[0095] The embodiments provided in this application can determine the basic cutter wear model by combining the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient. Based on the basic cutter wear model, the wear of the cutter can be predicted, thereby improving the accuracy of cutter wear prediction under soil-rock interfacial strata conditions.

[0096] In step 104, the cumulative wear of the cutterhead can be predicted based on the shield tunneling ring number and the basic cutterhead wear model.

[0097] In some implementations, the parameters of any ring excavated by the tunnel boring machine are input into the wear model of the foundation cutter head to obtain the radial wear of the cutter head when excavating any ring, wherein the parameters correspond to the parameters in the wear model of the foundation cutter head;

[0098] Then, the cumulative wear of the hob can be predicted using formula (8);

[0099] Equation (8) can be expressed as:

[0100]

[0101] Among them, w m w represents the cumulative wear of the cutterhead after excavating m rings, where m is the number of shield excavation rings. i This represents the radial wear of the cutter head during the excavation of the i-th ring.

[0102] Optionally, the parameters of any ring being excavated by the tunnel boring machine can be input into the basic cutter wear model to obtain the radial wear of the cutter when excavating any ring. That is, the cutter wear caused during the excavation of the i-th ring can be calculated in units of rings and can be expressed by formula (9).

[0103]

[0104] Among them, w i p represents the radial wear of the cutter during the excavation of the i-th ring; R is the cutter installation radius; i x represents the penetration depth when excavating the i-th ring; i L represents the height of the soil-rock interface during the excavation of the i-th ring; i P represents the forward distance of the tunnel boring machine during the construction of the i-th ring; iThis represents the contact pressure between the cutter head and the excavated soil during the excavation of the i-th ring. It should be understood that in this application, the same symbols represent the same meaning. Therefore, the meaning of the symbols not explained in formula (9) can be found in the explanations in other parts of this application.

[0105] Please refer to Figure 2 , Figure 2 This is a coordinate graph showing the predicted hob wear amount provided in some embodiments of this application. Figure 2 In the graph, the horizontal axis represents the measured value of wear, and the vertical axis represents the predicted value of wear. Both are in millimeters (mm). The correlation index is 0.77. Hollow circles represent hob wear. It should be understood that the closer the hob wear is to the 45° diagonal of the coordinate axis, the closer the predicted wear result is to the measured value.

[0106] pass Figure 2 It can be seen that the wear amount predicted by the cutter wear prediction method provided in this application is distributed near the 45° diagonal line in the coordinate axis. That is, the cutter wear prediction method of the embodiment of this application improves the accuracy of cutter wear prediction under soil-rock strata conditions.

[0107] The above is an introduction to an embodiment of the hob wear prediction method of this application.

[0108] The implementation of the hob wear prediction device provided in this application will now be described in detail with reference to the accompanying drawings.

[0109] In addition to the hob wear prediction method provided in the above embodiments, this application also provides a hob wear prediction device for implementing the above method, such as... Figure 3 As shown, Figure 3 This is a schematic block diagram of a hob wear prediction device according to an embodiment of this application. The hob wear prediction device 300 includes:

[0110] The first determining module 301 is used to determine the first positive force on the rock being crushed by the roller cutter through the rock strength, penetration depth and the geometric parameters of the roller cutter;

[0111] The second determining module 302 is used to determine the second positive force on the soil layer when the roller cutter slides and cuts through the geometric parameters of the roller cutter, internal friction angle, cohesion, penetration and the mechanical interaction between the roller cutter and the slag.

[0112] The third determining module 303 is used to determine the wear amount model of the basic cutter based on the sum of the first energy action of the cutter in the rock layer and the second energy action of the cutter in the soil layer, the cutter ring hardness and wear coefficient. The first energy action is expressed as the product of the first positive force and the sliding distance of the cutter in the rock layer, and the second energy action is expressed as the product of the second positive force and the sliding distance of the cutter in the soil layer.

[0113] The prediction module 304 is used to predict the cumulative wear of the cutter head based on the number of tunneling rings and the cutter head wear model.

[0114] It is understood that the content of the above method embodiments is applicable to the present device embodiments. The specific functions implemented by the present device embodiments are the same as those of the above method embodiments, and the beneficial effects achieved are also the same as those achieved by the above method embodiments.

[0115] like Figure 4 As shown, this application embodiment also provides an electronic device 400, which includes a memory 401 and one or more processors 402. Figure 4 (Only one is shown in the image) and a computer program stored in memory 401 and executable on processor 402. Memory 401 stores software programs and units; processor 402 executes various functional applications and data processing by running the software programs and units stored in memory to obtain resources corresponding to the aforementioned preset events. Optionally, processor 402 implements the aforementioned method for predicting hob wear by running the aforementioned computer program stored in memory 401.

[0116] Memory 401 serves as a non-transitory computer-readable medium for storing non-transitory software programs and non-transitory computer-executable programs. Furthermore, memory 401 may include high-speed random access memory and may also include non-transitory memory, such as at least one disk storage device, flash memory device, or other non-transitory solid-state storage device. In some embodiments, memory 401 may include memory remotely located relative to processor 402, and this remote memory may be connected to the processor via a network.

[0117] It is understood that the content of the above method embodiments is applicable to the embodiments of this electronic device. The specific functions implemented by the embodiments of this electronic device are the same as those of the above method embodiments, and the beneficial effects achieved are also the same as those achieved by the above method embodiments.

[0118] This application also provides a tunnel boring machine (TBM) that predicts cutter wear using the aforementioned cutter wear prediction device or the aforementioned electronic device.

[0119] It is understood that the content of the above method embodiments is applicable to this shield machine embodiment. The specific functions implemented in this shield machine embodiment are the same as those in the above method embodiments, and the beneficial effects achieved are also the same as those achieved in the above method embodiments.

[0120] This application also provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the above-described method for predicting hob wear.

[0121] It is understood that the content of the above method embodiments is applicable to this storage medium embodiment. The specific functions implemented in this storage medium embodiment are the same as those in the above method embodiments, and the beneficial effects achieved are also the same as those achieved in the above method embodiments.

[0122] This application also provides a computer program product, which includes a computer program that, when executed by one or more processors, can implement the steps of the above-described method for predicting hob wear.

[0123] It is understood that the content of the above method embodiments is applicable to this computer program product. The specific functions implemented by the embodiments of this computer program product are the same as those of the above method embodiments, and the beneficial effects achieved are also the same as those achieved by the above method embodiments.

[0124] The cutter wear prediction method, device, electronic equipment, tunnel boring machine, medium, and computer program product provided in this application fully consider the energy effects of the cutter in the rock and soil layers, the sum of the first energy effect of the cutter in the rock layer and the second energy effect of the cutter in the soil layer, the cutter ring hardness, and the wear coefficient. The basic cutter wear model determined by combining the two fully considers the energy effects of the cutter in the rock and soil layers. The basic cutter wear model constructed by combining the two and the cumulative wear of the cutter predicted by the number of tunnel boring rings has a smaller error with the actual wear of the cutter compared with related cutter wear prediction methods, thereby improving the accuracy of cutter wear prediction.

[0125] The embodiments described in this application are for the purpose of more clearly illustrating the technical solutions of the embodiments of this application, and do not constitute a limitation on the technical solutions provided by the embodiments of this application. As those skilled in the art will know, with the evolution of technology and the emergence of new application scenarios, the technical solutions provided by the embodiments of this application are also applicable to similar technical problems.

[0126] Although specific embodiments are described herein, those skilled in the art will recognize that many other modifications or alternative embodiments are also within the scope of this disclosure. For example, any of the functions and / or processing capabilities described in connection with a particular device or component can be performed by any other device or component. Furthermore, while various exemplary embodiments and architectures have been described according to embodiments of this disclosure, those skilled in the art will recognize that many other modifications to the exemplary embodiments and architectures described herein are also within the scope of this disclosure.

[0127] The foregoing description, with reference to block diagrams and flowcharts of systems, methods, systems, and / or computer program products according to exemplary embodiments, has described certain aspects of this disclosure. It should be understood that one or more blocks in the block diagrams and flowcharts, as well as combinations of blocks in the block diagrams and flowcharts, can be implemented by executing computer-executable program instructions, respectively. Similarly, according to some embodiments, some blocks in the block diagrams and flowcharts may not need to be executed in the order shown, or may not all need to be executed. Furthermore, additional components and / or operations beyond those shown in the blocks in the block diagrams and flowcharts may exist in some embodiments.

[0128] Therefore, blocks in block diagrams and flowcharts support combinations of means for performing a specified function, combinations of elements or steps for performing a specified function, and program instruction means for performing a specified function. It should also be understood that each block in a block diagram and flowchart, and combinations of blocks in block diagrams and flowcharts, can be implemented by a dedicated hardware computer system or a combination of dedicated hardware and computer instructions that performs a specific function, element, or step.

[0129] The program modules, applications, etc., described herein may include one or more software components, including, for example, software objects, methods, data structures, etc. Each such software component may include computer-executable instructions that, in response to execution, cause at least a portion of the functionality described herein (e.g., one or more operations of the exemplary methods described herein) to be performed.

[0130] Software components can be coded using any of a variety of programming languages. An exemplary programming language could be a low-level programming language, such as assembly language associated with a specific hardware architecture and / or operating system platform. Software components including assembly language instructions may need to be converted into executable machine code by an assembler before being executed by the hardware architecture and / or platform. Another exemplary programming language could be a higher-level programming language that is portable across multiple architectures. Software components including higher-level programming languages ​​may need to be converted into an intermediate representation by an interpreter or compiler before execution. Other examples of programming languages ​​include, but are not limited to, macro languages, shell or command languages, job control languages, scripting languages, database query or search languages, or report writing languages. In one or more exemplary embodiments, a software component containing instructions from one of the above-described programming language examples can be executed directly by the operating system or other software components without first being converted into another form.

[0131] Software components can be stored as files or other data storage structures. Software components of similar type or related function can be stored together in a specific directory, folder, or library. Software components can be static (e.g., pre-defined or fixed) or dynamic (e.g., created or modified at runtime).

[0132] The embodiments of this application have been described in detail above with reference to the accompanying drawings. However, this application is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of this application.

Claims

1. A method of predicting an amount of wear of a rolling cutter, characterized by, The method comprises the following steps: determining a first normal force acting on the roller cutter for rolling and breaking rock through rock strength, penetration and geometric parameters of the roller cutter; determining a second normal force acting on the roller cutter for sliding and cutting soil through the geometric parameters of the roller cutter, internal friction angle, cohesive force, penetration and mechanical action between the roller cutter and the soil; determining a basic roller cutter wear amount model based on a sum of a first energy action of the roller cutter in rock and a second energy action of the roller cutter in soil, hardness of a cutter ring of the roller cutter and a wear coefficient, wherein the first energy action is represented as a product of the first normal force and a sliding distance of the roller cutter in rock, and the second energy action is represented as a product of the second normal force and a sliding distance of the roller cutter in soil; predicting a cumulative wear amount of the roller cutter according to a number of shield tunneling rings and the basic roller cutter wear amount model; wherein the geometric parameters of the roller cutter include a roller cutter radius, a roller cutter ring blade angle, a roller cutter blade width and a cutter spacing, the rock strength includes rock uniaxial compressive strength and rock tensile strength, and the mechanical action between the roller cutter and the soil includes contact pressure between the roller cutter and the soil; the determining of the first normal force acting on the roller cutter for rolling and breaking rock through the rock strength, the penetration and the geometric parameters of the roller cutter comprises determining the first normal force through a quotient of a first algorithm and the roller cutter blade width, wherein the first algorithm is determined through a product of a power of a first sub-algorithm, a power of the roller cutter radius, a power of the rock uniaxial compressive strength and a power of the roller cutter blade width, and the first sub-algorithm is represented through a product of the cutter spacing, the penetration and the rock tensile strength; the determining of the second normal force acting on the roller cutter for sliding and cutting soil through the geometric parameters of the roller cutter, the internal friction angle, the cohesive force, the penetration and the mechanical action between the roller cutter and the soil comprises: determining the second normal force acting on the roller cutter for sliding and cutting soil through a second algorithm; the second algorithm is represented as: wherein, represents the second normal force, represents the sliding friction coefficient between the roller cutter and the rock, r represents the roller cutter radius, p is the roller cutter penetration, P is the contact pressure between the roller cutter and the muck, is the internal friction angle, c 0 is the cohesion, is the roller cutter rim angle, in n represents the normal force, in s represents the sliding.

2. The method of predicting the wear amount of a rolling cutter according to claim 1, characterized by, the determining of the basic roller cutter wear amount model based on the sum of the first energy action of the roller cutter in rock and the second energy action of the roller cutter in soil, the hardness of the cutter ring of the roller cutter and the wear coefficient comprises: determining the basic roller cutter wear amount model through a third algorithm; the third algorithm is represented as: wherein, is the base amount of cutter wear, k s is the wear coefficient, H is the hardness of the cutter ring, is the first normal force, is the sliding distance of the cutter in the rock formation, is the second normal force, is the sliding distance of the cutter in the soil formation, n in the equation represents the normal force, r in the equation represents the rolling.

3. The method of predicting the wear amount of a rolling cutter according to claim 2, characterized by, the prediction method of the wear amount of the roller cutter further comprises determining the hardness of the cutter ring of the roller cutter, and the determining of the hardness of the cutter ring of the roller cutter comprises: measuring hardnesses of a plurality of different positions uniformly distributed in a ring direction of the cutter ring to obtain a plurality of initial cutter ring hardnesses; determining an average value of the plurality of initial cutter ring hardnesses; determining the average value as the hardness of the cutter ring of the roller cutter.

4. The method of predicting the wear amount of a rolling cutter according to claim 1, characterized by, the predicting of the cumulative wear amount of the roller cutter according to the number of shield tunneling rings and the basic roller cutter wear amount model comprises: inputting parameters of tunneling of any ring of a shield tunneling machine into the basic roller cutter wear amount model to obtain a radial wear amount of the roller cutter when tunneling any ring, wherein the parameters correspond to parameters in the basic roller cutter wear amount model; predicting the cumulative wear amount of the roller cutter through a fourth algorithm; the fourth algorithm is represented as: wherein, is the cumulative wear amount of the ring cutter, m is the cumulative wear amount of the ring cutter, m is the cumulative wear amount of the ring cutter, is the cumulative wear amount of the ring cutter, i is the cumulative wear amount of the ring cutter.

5. The method of predicting the wear amount of a rolling cutter according to Claim 1, wherein The method for predicting the cutter wear amount further comprises: The sliding distance of the cutter in the rock layer and the soil layer is determined according to the penetration, the cutter radius, the installation radius of the cutter, the advancing distance of one ring of tunneling of the shield machine, the shield excavation diameter and the height of the soil-rock interface.

6. A device for predicting the amount of wear of a hob, characterized in that The device comprises: The first determining module is configured to determine a first normal force borne by the cutter for rolling and breaking rock through rock strength, penetration and geometric parameters of the cutter; The second determining module is configured to determine a second normal force borne by the cutter for sliding and cutting soil through geometric parameters of the cutter, internal friction angle, cohesion, penetration and mechanical action between the cutter and muck; The third determining module is configured to determine a basic cutter wear amount model based on a sum of a first energy action of the cutter in the rock layer and a second energy action of the cutter in the soil layer, hardness of a cutter ring of the cutter and a wear coefficient, wherein the first energy action is represented as a product of the first normal force and the sliding distance of the cutter in the rock layer, and the second energy action is represented as a product of the second normal force and the sliding distance of the cutter in the soil layer; The predicting module is configured to predict a cumulative wear amount of the cutter according to a number of tunneling rings of the shield and the basic cutter wear amount model; The geometric parameters of the cutter include cutter radius, cutter ring blade angle, cutter blade width and cutter spacing, the rock strength includes rock uniaxial compressive strength and rock tensile strength, and the mechanical action between the cutter and muck includes contact pressure between the cutter and muck; The first normal force borne by the cutter for rolling and breaking rock is determined through a quotient of a first algorithm and the cutter blade width, wherein the first algorithm is determined through a product of a power of a first sub-algorithm, a power of the cutter radius, a power of the rock uniaxial compressive strength and a power of the cutter blade width, and the first sub-algorithm is represented through a product of the cutter spacing, the penetration and the rock tensile strength; The second normal force borne by the cutter for sliding and cutting soil is determined through a second algorithm; The second algorithm is represented as: The electronic device comprises a memory and a processor, the memory stores a computer program, and the processor implements the method for predicting the cutter wear amount according to any one of claims 1 to 5 when executing the computer program. wherein, represents the second normal force, represents the sliding friction coefficient between the roller cutter and the rock, r represents the roller cutter radius, p is the roller cutter penetration, P is the contact pressure between the roller cutter and the muck, is the internal friction angle, c 0 is the cohesion, is the roller cutter gage angle, in n represents the normal force, in s represents the sliding.

7. An electronic device, comprising: 8.A shield machine, wherein a cutter wear amount of the cutter in the shield machine is predicted by the device for predicting the cutter wear amount according to claim 6 or the electronic device according to claim 7. ​

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