CN113779679B - Hard rock shield or TBM technical parameter model selection method and system - Google Patents

Hard rock shield or TBM technical parameter model selection method and system Download PDF

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CN113779679B
CN113779679B CN202111076360.6A CN202111076360A CN113779679B CN 113779679 B CN113779679 B CN 113779679B CN 202111076360 A CN202111076360 A CN 202111076360A CN 113779679 B CN113779679 B CN 113779679B
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cutter head
calculation formula
thrust
torque
weight
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CN113779679A (en
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李建
田晓阳
李先重
吴圣智
李宏伟
邴召建
苏雷
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Shandong Jianzhu University
Shandong Hi Speed Engineering Construction Group Co Ltd
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Shandong Jianzhu University
Shandong Hi Speed Engineering Construction Group Co Ltd
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    • G06—COMPUTING; CALCULATING OR COUNTING
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    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/13—Architectural design, e.g. computer-aided architectural design [CAAD] related to design of buildings, bridges, landscapes, production plants or roads
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
    • G06F2111/10—Numerical modelling
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

Abstract

The invention provides a hard rock shield or TBM technical parameter type selection method, which comprises the steps of obtaining geological parameters of a construction site, tunnel design parameters, elastic modulus of various surrounding rocks, Poisson's ratio and radius of a cutter head; calculating the weight of the cutter head according to a cutter head weight semi-empirical calculation formula; and obtaining the thrust of the main thrust oil cylinder according to a calculation formula of the main thrust oil cylinder, obtaining the thrust of the auxiliary thrust oil cylinder according to a calculation formula of the auxiliary thrust oil cylinder, and obtaining the cutter head escaping torque according to a calculation formula of the cutter head escaping torque. And considering the coordinated deformation of the cutter head and the surrounding rock, establishing a corresponding relation between the weight of the cutter head and the quality of the surrounding rock, and providing a semi-empirical calculation formula of the weight of the cutter head through engineering research to guide the weight design of the cutter head.

Description

Hard rock shield or TBM technical parameter type selection method and system
Technical Field
The disclosure relates to the field of rail transit engineering, in particular to a hard rock shield or TBM technical parameter model selection method and system.
Background
The statements in this section merely provide background information related to the present disclosure and may not necessarily constitute prior art.
In recent years, more and more rock subway tunnels are beginning to be constructed by adopting TBM or hard rock shield. The shield tunneling machine has the advantages that the geological conditions are different, the applicability of the hard rock shield or TBM is different, and reasonable selection of main technical parameters of the shield or TBM has important influences on guaranteeing construction safety and improving construction efficiency. At present, when a subway tunnel hard rock shield or TBM is subjected to model selection, a model selection mainly depends on an engineering comparison method or an expert survey method, and a corresponding theoretical support, particularly a main technical parameter theoretical model selection method based on geological features, is lacked. The tunneling of the hard rock shield or the TBM is actually a process of interaction between machinery and surrounding rocks, and obviously, in the selection of main technical parameters of mechanical equipment, the interaction relationship between the surrounding rocks and the mechanical equipment should be considered. On the basis of the interaction relation between the surrounding rock and mechanical equipment, the model selection method which takes the main technical parameters of weight, thrust, torque and the like of the cutterhead under geological conditions into consideration is important for the safe and efficient tunneling of the hard rock shield or the TBM.
Disclosure of Invention
The invention aims to solve the problems and provides a hard rock shield or TBM technical parameter model selection method and system.
According to some embodiments, the following technical scheme is adopted in the disclosure:
a hard rock shield or TBM technical parameter type selection method comprises the following steps:
acquiring geological parameters of a construction site, tunnel design parameters, elastic modulus of various surrounding rocks, Poisson's ratio and radius of a cutter head;
calculating a cutter weight according to the obtained parameters and a cutter weight semi-empirical formula;
obtaining the thrust of the main push oil cylinder according to the obtained parameters and a calculation formula of the main push oil cylinder, and obtaining the thrust of the auxiliary push oil cylinder according to a calculation formula of the auxiliary push oil cylinder;
and obtaining the cutter head escaping torque according to the obtained parameters and a cutter head escaping torque calculation formula.
Further, the weight semi-empirical calculation formula of the cutter head is as follows:
Figure BDA0003262346210000021
wherein R is a radius, Er、vrRespectively the modulus of elasticity and the poisson ratio of the rock mass.
Further, the calculation formula of the main thrust cylinder is as follows:
Fmaster and slave＝Fr+Ff1+Ff2，
Wherein Fr is the thrust of the main thrust cylinder and should consider the rock breaking force of a cutter head and Ff1Is the friction force of the shield Ff2Is the self-weight friction force.
Further, the calculation formula of the auxiliary push oil cylinder is as follows:
Fauxiliary device＝S+Fr+Ff1+Ff2+Ff3，
Wherein S is the face extrusion force, Fr is the cutter breaking force, Ff1Is the friction force of the shield Ff2Is the machine friction force, Ff3The friction force between the rear matching body and the track.
Further, the cutter head out-of-service torque calculation formula is as follows:
Tx＝Td1+Td2+Td3
td1 represents the friction torque in front of the cutter head, Td2 represents the rotational resistance torque of the hob, and Td3 represents the friction torque at the edge of the cutter head.
Further, the semi-empirical calculation formula of the weight of the cutterhead is based on consideration of the coordinated deformation of the cutterhead and the surrounding rock, the corresponding relation between the weight of the cutterhead and the quality of the surrounding rock is established, and the semi-empirical calculation formula of the weight of the cutterhead is provided through engineering research to guide the weight design of the cutterhead.
Furthermore, a cutter head escaping torque calculation formula is based on the fact that a cutter head is clamped, and the escaping torque is considered to be larger than the cutter head resisting torque caused by overcoming unfavorable geological conditions.
A hard rock shield or TBM technical parameter type selection system comprises:
the data acquisition module is configured to acquire construction site geological parameters and tunnel design parameters, and elastic modulus, Poisson's ratio and radius of the cutter head of various kinds of surrounding rocks;
the cutter head weight module is configured to obtain the cutter head weight according to a cutter head weight semi-empirical calculation formula;
the thrust calculation module is configured to obtain the thrust of the main thrust cylinder according to a main thrust cylinder calculation formula and obtain the thrust of the auxiliary thrust cylinder according to an auxiliary thrust cylinder calculation formula;
and the de-trapping torque module is configured to obtain the cutter head de-trapping torque according to a cutter head de-trapping torque calculation formula.
A computer readable storage medium having stored therein a plurality of instructions adapted to be loaded by a processor of a terminal device and to execute a hard rock shield or TBM technique parameter typing method as described.
A terminal device comprising a processor and a computer readable storage medium, the processor being configured to implement instructions; the computer readable storage medium is used for storing a plurality of instructions, and the instructions are suitable for being loaded by a processor and executing the hard rock shield or TBM technical parameter model selection method.
Compared with the prior art, the beneficial effect of this disclosure is:
the method comprises the steps of considering the coordinated deformation of a cutter head and surrounding rocks, establishing a corresponding relation between the weight of the cutter head and the quality of the surrounding rocks, and providing a semi-empirical calculation formula of the weight of the cutter head through engineering investigation to guide the weight design of the cutter head;
the total thrust is divided into auxiliary thrust cylinder thrust and main thrust cylinder thrust, the main thrust cylinder mainly breaks rocks, the main thrust cylinder breaks hard rocks, and a main thrust cylinder calculation formula is established. The auxiliary thrust cylinder is mainly used for escaping from the trouble, and a method for calculating escaping thrust during blocking is provided on the basis of the most unstable surrounding rock;
the cutter head escaping torque is mainly used for clamping the cutter head, and a cutter head escaping torque calculation method is established by considering that the escaping torque is larger than the cutter head resistance torque caused by overcoming unfavorable geological conditions.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the application and, together with the description, serve to explain the application and are not intended to limit the application.
FIG. 1 is a diagram of the interaction of the cutterhead and surrounding rock of the present embodiment;
FIG. 2 is a force deformation diagram of the cutter head of the embodiment;
FIG. 3 is a wall rock force deformation diagram of the present embodiment;
FIG. 4 shows the present embodiment
Figure BDA0003262346210000041
A relation graph with the weight Pd of the cutter head;
FIG. 5 is a graph of force analysis of the hob in this embodiment;
FIG. 6 is a Mohr stress circle plot for the rock unit cell of this example;
FIG. 7 is a diagram of a model for calculating soil pressure according to the present embodiment;
FIG. 8 is a diagram of a three-dimensional wedge calculation model according to the embodiment;
fig. 9 is a force analysis diagram of the palm-face wedge of the present embodiment.
The specific implementation mode is as follows:
the present disclosure is further described with reference to the following drawings and examples.
It should be noted that the following detailed description is exemplary and is intended to provide further explanation of the disclosure. Unless defined otherwise, 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.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
As shown in fig. 1, a hard rock shield or TBM technical parameter model selection method includes the following steps:
acquiring geological parameters of a construction site, tunnel design parameters, elastic modulus of various surrounding rocks, Poisson's ratio and radius of a cutter head;
calculating the weight of the cutter head according to a cutter head weight semi-empirical calculation formula;
obtaining the thrust of the main thrust oil cylinder according to a calculation formula of the main thrust oil cylinder, and obtaining the thrust of the auxiliary thrust oil cylinder according to a calculation formula of the auxiliary thrust oil cylinder;
and obtaining the cutter head overcoming torque according to a cutter head overcoming torque calculation formula.
The method comprises the following specific steps:
(1) weight model selection method for cutter head based on rock rigidity
The hard rock shield or TBM rock breaking process is a process of interaction between a cutter head and surrounding rock, and the cutter head and the surrounding rock deform in a coordinated manner in the process. The deformation of the cutter head is related to the rigidity of the cutter head, and the deformation of the surrounding rock is related to the rigidity of the surrounding rock. In contrast, the relationship between the cutter stiffness design and the geological condition can be obtained based on the coordination deformation relationship between the cutter and the surrounding rock.
Firstly, deformation of cutter head
Supposing the cutter head of the full-face rock tunnel boring machine to be an elastic thin plate, and bearing the uniform rock load q by the cutter head0. The cutter head displacement w being a function of r only, the cutterThe elastic surface differential equation in the disc can be written as:
Figure BDA0003262346210000051
in the formula, D is the bending rigidity of the cutter head, and r is the radius from any point on the cutter head to the circle center.
The cutter head deformation equation is solved as follows:
w＝C1lnr+C2r2lnr+C3r2+C4+w1 (2)
wherein, w1For any special solution of a differential equation, for a thin plate which is uniformly loaded with q,
Figure BDA0003262346210000061
considering that the center of the cutter head is generally provided with a central hob and a cutter head bearing mounting seat hole is arranged behind the box-shaped cutter head, therefore:
C1＝C2＝0 (3)
after the cutter head is stressed, the ordinary differential equation of the cutter head bending can be written as follows:
Figure BDA0003262346210000062
when the connection relationship between the cutter bearing and the cutter is clamping, the following steps are provided:
Figure BDA0003262346210000063
wherein, the supporting radius of the cutter head bearing is R0
Thus, one can obtain:
Figure BDA0003262346210000064
when the connection relation between the cutter head bearing and the cutter head is simple support, the following steps are provided:
Figure BDA0003262346210000065
the following can be obtained:
Figure BDA0003262346210000066
r is the actual radius of the cutter head, R0where/R is a constant value and u is the Poisson's ratio, the variation is small and is regarded as a constant.
R/R is relative position, let k1R/R, then the above formulas (6), (8) may be considered together as the following expression:
Figure BDA0003262346210000071
equation for rock deformation
The load concentration of the disc cutter on the face caused by the thrust of the cutter head is set as uniform load q1. The stress on the tunnel face is simplified into a model with uniformly distributed pressure in the circular area of the surface of the semi-space body. The actual radius of the cutter head is R, and a surface displacement expression of the semi-infinite body can be obtained according to a classical elastic mechanics solution, wherein the surface displacement expression is as follows:
Figure BDA0003262346210000072
in the above formula, Er、vrRespectively the modulus of elasticity and poisson ratio of the rock mass.
Will k1R/R into (10) may be obtained:
Figure BDA0003262346210000073
disc weight calculation formula
According to the coordinated deformation of the cutter head and the surrounding rock, the simultaneous formulas (9) and (11) eliminate w (k)1) Andq1the following can be obtained:
Figure BDA0003262346210000074
d is the bending rigidity of the cutter head, and the expression is as follows:
Figure BDA0003262346210000075
in the above formula, E, u are the elastic modulus and poisson ratio of the cutter head, respectively, and can be regarded as constants; d is the thickness of the cutter head. Substituting formula (13) into formula (11) yields:
Figure BDA0003262346210000076
in the above formula, f1(k1)、f2(k1)Is a function of relative position.
The difference of hard rock shield or TBM cutterhead materials is small, and the elasticity modulus and Poisson ratio related to the characteristics of the cutterhead materials can be regarded as constants; the thickness of the cutter head and the radius of the cutter head are related to the design and are regarded as variables; the variability of geological conditions is large and is related to the cutter head design, so the elastic modulus and the Poisson ratio of the geological conditions are regarded as variables. Placing all variables to the left of the equation and constants to the right of the equation gives:
Figure BDA0003262346210000081
using a constant C to the right of the equal sign3To show that:
Figure BDA0003262346210000082
considering the weight of the cutter head as gammadThe weight calculation formula of the cutter head is as follows:
Figure BDA0003262346210000083
c pi gamma in the above formuladExpressed by the coefficient C1, the above equation can be simplified to:
Figure BDA0003262346210000084
collecting similar engineering cases, and determining coefficient C by adopting statistical regression method1。
Therefore, the relation of the weight of the cutter head is as follows:
Figure BDA0003262346210000085
in the above formula, the radius R is expressed in units of (m); the unit of Er is GPa; the weight of the cutter head Pd is ton.
(2) Total thrust design method
Thrust calculation method for main thrust oil cylinder
The main push oil cylinder mainly breaks rock, and the thrust of the main push oil cylinder takes the rock breaking force Fr of a cutter head and the friction force F of a shield into considerationf1Self-weight friction force Ff2。
FMaster and slave＝Fr+Ff1+Ff2 (20)
A. Rock breaking force of cutter head
The thrust of the cutter head for breaking rock is the stress set of each hob and mainly comes from the rock resistance suffered by the hob when the hob breaks rock. The force applied by the individual roller cutters is shown in figure 5.
The hob is approximated as pure rolling, only the radial force (towards the centre of the hob) σ on the rock-contacting surface of the hob is taken into account1Neglecting tangential forces, the lateral surface of the rock unit body is subjected to a confining pressure σ perpendicular to this surface3. During the tunneling process, the rock is crushed by the rolling action of the hob, and mainly subjected to shearing damage in a pressed state. Based on Mohr-Coulomb's law, the maximum shear stress that the rock unit body can bear is determined by cohesive force and internal friction angle:
Figure BDA0003262346210000091
wherein τ is the shear stress (MPa) on the fracture plane; c is the rock cohesion (MPa); σ is the positive stress (MPa) on the failure plane;
Figure BDA0003262346210000092
is the rock internal friction angle (rad).
FIG. 6 shows the Moore stress circle of the unit cell, from which the radial ultimate contact pressure of the rock can be calculated as
Figure BDA0003262346210000093
In the formula, σcThe uniaxial compressive strength (MPa) of the rock, i.e. the ultimate stress when not confined.
Because the radial stress on the contact arc surface is approximately and uniformly distributed, the limit contact pressure of the rock unit body is integrated along the contact arc surface to obtain an approximate calculation formula of the rock breaking force of the hob, wherein the approximate calculation formula is
Figure BDA0003262346210000094
Wherein Fn is a tunneling direction rock breaking force (kN); t is the width (mm) of the knife tip; r is the cutter radius (mm); θ is the contact pressure and vertical angle (rad); phi is the contact arc radian (rad). From the geometric relationship
Figure BDA0003262346210000101
The formula (22) is substituted for the formula (23) and integral calculation is completed, so that the rock breaking force of the hob in the tunneling direction can be obtained as
Figure BDA0003262346210000102
Because the underground depth is shallow, its confined pressure is less, consequently can not consider the country rock pressure, the above formula can simplify to:
Fn＝TRσcsinφ (25)
the TBM cutter head is usually provided with dozens of hobs, and all hobs are arranged in a staggered mode. Although the stress of the hobs at different positions at the same time is slightly different, when the overall stress of the cutterhead is analyzed from the statistical angle, the average stress of the hobs can be considered to be approximately equal, and the overall rock breaking force of the cutterhead can be approximately expressed as
Figure BDA0003262346210000103
B. Friction of shield
In order to reduce the vibration of the machine head and prevent the shield from being stuck, the position of the shield is timely adjusted by the tunneling machine during operation in the stratum, so that the friction force for blocking relative movement exists between the contact surface of the shield and the surrounding rock of the tunnel wall by the outer circumferential surface of the shield with smaller pressure, and the friction force is related to the contact pressure, the friction factor and the shield size.
Ff1＝u1pA (27)
In the formula: u. of1The friction force between the surrounding rock and the shield is usually 0.2-0.3; p is the contact pressure of the surrounding rock and the shield; a is the contact area of the shield and the surrounding rock, and the shield mainly considers a front shield and a connecting shield.
The contact pressure of the surrounding rock and the shield mainly comprises active soil pressure and passive soil pressure, the active soil pressure is considered above and at two sides of the shield and is calculated according to a shallow tunnel Shexijia soil pressure calculation formula, the passive soil pressure of the lower structure is considered to be the same as the upper load, and a soil pressure load calculation model is shown in figure 7.
C. Friction of machine
Mechanical friction is related to mechanical weight.
Ff2＝u1G1 (27)
In the formula: g1 is the machine weight.
Thrust calculation method for auxiliary thrust oil cylinder
Auxiliary push oil cylinderThe auxiliary oil cylinder is mainly used for tunneling in a single shield mode in a weak and broken stratum, and the auxiliary oil cylinder is guaranteed to provide a thrust force meeting the requirement that a machine is not blocked during construction under a fault broken zone. The auxiliary oil cylinder mainly bears the following loads: face extrusion force S, cutter head rock breaking force Fr and shield friction force Ff1Machine friction force Ff2The friction force F of the rear matching and the trackf3。
FAuxiliary device＝S+Fr+Ff1+Ff2+Ff3 (28)
The uniaxial compressive strength of the rock mass in the weak surrounding rock is smaller, and the required rock breaking force of the cutter head is smaller, so that the rock breaking force of the cutter head can be ignored in the design of the thrust of the auxiliary oil cylinder, and the thrust of the auxiliary oil cylinder mainly bears the extrusion force of the tunnel face and the frictional resistance in the advancing process of the TBM.
FAuxiliary device＝S+Ff1+Ff2+Ff3 (29)
The friction resistance of the rear matching is mainly related to the weight of the rear matching and the friction coefficient between the machine and the track:
Ff3＝u2G2 (30)
in the formula: u. of2The friction coefficient between the machine and the rail is usually 0.1-0.3; g2The weight of the rear matching.
And the calculation of the palm surface extrusion force S is combined with a three-dimensional wedge body calculation model for analysis. The three-dimensional wedge calculation model for horns is shown in figure 8.
The wedge ABCDJI was removed and the force analysis was shown in FIG. 9.
The load on the wedge is:
Figure BDA0003262346210000121
d is the diameter of tunnel excavation
The self-weight of the wedge-shaped body is as follows:
Figure BDA0003262346210000122
assuming that the vertical stress of the wedge block is linearly distributed along the depth, the side shearing force of the wedge body can be obtained as follows:
Figure BDA0003262346210000123
according to the molar coulomb criterion, the shear forces on the inclined plane are:
Figure BDA0003262346210000124
balanced by horizontal and vertical forces
S+Tccosα+2Tscosα＝Nsinα (35)
P+G＝Tcsinα+2Tssinα+Ncosα (36)
The equation for the face support force can be obtained as follows:
Figure BDA0003262346210000125
(3) design method of torque for escaping from poverty
The reason that the cutter head cannot rotate in the subway tunnel to cause the blockage of the cutter head is that the maximum torque which can be provided by the cutter head cannot overcome the resistance torque of the cutter head caused by unfavorable geological conditions. When the cutter head rotates, 3 aspects of torque need to be overcome: a friction torque Td1 in front of the cutter; rotating resistance moment Td2 of the hob; ③ the friction moment Td3 of the edge of the cutter head. The total torque Tx that the cutter head must overcome is:
Tx＝Td1+Td2+Td3 (38)
the calculation methods of the moments in the above 3 aspects are respectively as follows:
front friction torque of cutter
Assuming that the face extrusion force S is acting on the face of the cutterhead on average, then the vertical stress on the cutterhead face, σ dv, is expressed as:
Figure BDA0003262346210000131
therefore, the tangential stress generated by the broken surrounding rock at any point of the cutter head and opposite to the rotation direction of the cutter head is as follows:
Figure BDA0003262346210000132
mu in the formula is the friction coefficient of the surrounding rock and the cutter head, the friction coefficient of the surrounding rock and the cutter head in front of the tunnel face is different with different surrounding rock conditions, and the friction coefficient of the surrounding rock and the cutter head in a general fault fracture zone is 0.3. The total resistance torque generated by the contact of the cutter head surface and the broken surrounding rock is as follows:
Figure BDA0003262346210000133
② rotary resistance moment of hob
The rotary resistance torque of the hob is expressed as follows:
Figure BDA0003262346210000134
in the above formula, mu 2 is the resistance coefficient of the hob, and is generally 0.15-0.20; n is the number of the hobs on the cutter head; fi is acting force on the single hob; ri is the radius of gyration of each hob on the cutter head.
③ friction moment at edge of cutter head
Assuming that the average value of the frictional stress acting on the cutter disc edge is the same as the pressing force of the cutter disc center, the frictional torque Td3 of the cutter disc edge is expressed as follows:
Figure BDA0003262346210000135
in the above formula, tdThe width of the cutterhead exposed outside the shield is indicated by other symbols as before.
Example 2.
A hard rock shield or TBM technical parameter type selection system comprises:
the data acquisition module is configured to acquire construction site geological parameters and tunnel design parameters, and elastic modulus, Poisson's ratio and radius of the cutter head of various kinds of surrounding rocks;
the cutter head weight module is configured to obtain the cutter head weight according to a cutter head weight semi-empirical calculation formula;
the thrust calculation module is configured to obtain the thrust of the main thrust cylinder according to a main thrust cylinder calculation formula and obtain the thrust of the auxiliary thrust cylinder according to an auxiliary thrust cylinder calculation formula;
and the de-trapping torque module is configured to obtain the cutter head de-trapping torque according to a cutter head de-trapping torque calculation formula.
Example 3.
A computer readable storage medium having stored therein a plurality of instructions adapted to be loaded by a processor of a terminal device and to execute a hard rock shield or TBM technique parameter typing method as described.
Example 4.
A terminal device comprising a processor and a computer readable storage medium, the processor being configured to implement instructions; the computer readable storage medium is used for storing a plurality of instructions, and the instructions are suitable for being loaded by a processor and executing the hard rock shield or TBM technical parameter type selection method.
As will be appreciated by one skilled in the art, embodiments of the present application may be provided as a method, system, or computer program product. Accordingly, the present application may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present application may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, and so forth) having computer-usable program code embodied therein.
The present application is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the application. It will be understood that each flow and/or block of the flow diagrams and/or block diagrams, and combinations of flows and/or blocks in the flow diagrams and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.
Although the present disclosure has been described with reference to specific embodiments, it should be understood that the scope of the present disclosure is not limited thereto, and those skilled in the art will appreciate that various modifications and changes can be made without departing from the spirit and scope of the present disclosure.

Claims (6)

1. A hard rock shield or TBM technical parameter model selection method is characterized by comprising the following steps:
acquiring geological parameters of a construction site, tunnel design parameters, elastic modulus of various surrounding rocks, Poisson's ratio and radius of a cutter head;
calculating a cutter weight according to the obtained parameters and a cutter weight semi-empirical formula;
obtaining the thrust of the main push oil cylinder according to the obtained parameters and a calculation formula of the main push oil cylinder, and obtaining the thrust of the auxiliary push oil cylinder according to a calculation formula of the auxiliary push oil cylinder;
obtaining a cutter head escaping torque according to the obtained parameters and a cutter head escaping torque calculation formula;
the weight semi-empirical calculation formula of the cutter head is as follows:
Figure FDA0003593136040000011
wherein R is a radius, Er、vrRespectively is the elastic modulus and poisson ratio of the rock mass;
the calculation formula of the main thrust oil cylinder is as follows:
Fmaster and slave＝Fr+Ff1+Ff2，
Wherein, FrThe rock breaking force and F of a cutter head are considered for the thrust of the main thrust oil cylinderf1Is the friction force of the shield Ff2Machine friction;
the auxiliary push oil cylinder has the calculation formula as follows:
Fauxiliary device＝S+Fr+Ff1+Ff2+Ff3，
Wherein S is palm face extrusion force, FrBreaking force for cutter head, Ff1Is the friction force of the shield Ff2Is the machine friction force, Ff3The friction force between the rear matching body and the track;
the cutter head escaping torque calculation formula is as follows:
Tx＝Td1+Td2+Td3
wherein, Td1Friction torque, T, in front of the cutter headd2Is the rotary resistance moment, T, of the hobd3Is the friction torque of the edge of the cutter head.
2. The hard rock shield or TBM technical parameter model selection method according to claim 1, wherein the semi-empirical calculation formula of the weight of the cutterhead is based on considering the coordinated deformation of the cutterhead and the surrounding rock, establishing the corresponding relation between the weight of the cutterhead and the quality of the surrounding rock, and providing the semi-empirical calculation formula of the weight of the cutterhead through engineering research to guide the weight design of the cutterhead.
3. The hard rock shield or TBM technical parameter model selection method according to claim 1, wherein the cutter head detrapping torque calculation formula is based on cutter head sticking, and considering that the detrapping torque should be larger than the cutter head resistance torque caused by overcoming unfavorable geological conditions.
4. A hard rock shield or TBM technical parameter type selection system is characterized by comprising:
the data acquisition module is configured to acquire construction site geological parameters and tunnel design parameters, and elastic modulus, Poisson's ratio and radius of the cutter head of various kinds of surrounding rocks;
the cutter head weight module is configured to obtain the cutter head weight according to a cutter head weight semi-empirical calculation formula;
the thrust calculation module is configured to obtain the thrust of the main thrust cylinder according to a main thrust cylinder calculation formula and obtain the thrust of the auxiliary thrust cylinder according to an auxiliary thrust cylinder calculation formula;
the tool head torque-escaping module is configured to obtain a tool head torque-escaping according to a tool head torque-escaping calculation formula;
the weight semi-empirical calculation formula of the cutter head is as follows:
Figure FDA0003593136040000021
wherein R is a radius, Er、vrRespectively is the elastic modulus and poisson ratio of the rock mass;
the calculation formula of the main thrust oil cylinder is as follows:
Fmaster and slave＝Fr+Ff1+Ff2，
Wherein Fr is the thrust of the main thrust cylinder and should consider the rock breaking force of a cutter head and Ff1Is the friction force of the shield Ff2Machine friction;
the auxiliary push oil cylinder has the calculation formula as follows:
Fauxiliary device＝S+Fr+Ff1+Ff2+Ff3，
Wherein S is the face extrusion force, FrBreaking force for cutter head, Ff1Is the friction force of the shield Ff2Is the machine friction force, Ff3The friction force between the rear matching body and the track;
the cutter head escaping torque calculation formula is as follows:
Tx＝Td1+Td2+Td3
wherein, Td1Friction torque, T, in front of the cutter headd2Is the rotary resistance moment, T, of the hobd3The friction moment of the edge of the cutter head.
5. A computer-readable storage medium characterized by: a plurality of instructions stored therein, the instructions adapted to be loaded by a processor of a terminal device and to perform a hard rock shield or TBM technique parameter profiling method of any one of claims 1 to 3.
6. A terminal device is characterized in that: the system comprises a processor and a computer readable storage medium, wherein the processor is used for realizing instructions; a computer readable storage medium for storing a plurality of instructions adapted to be loaded by a processor and to perform a hard rock shield or TBM technique parameter typing method as claimed in any one of claims 1 to 3.
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104732059A (en) * 2015-01-12 2015-06-24 天津大学 Method for calculating total thrust in hard rock TBM device tunneling process
CN108241780A (en) * 2017-12-29 2018-07-03 天津大学 Composite shield tunnels the computational methods of cutter head torque in ground mixes geology
CN110362899A (en) * 2019-07-01 2019-10-22 中铁隧道局集团有限公司 The cutter head torque calculation method of basement rock protrusion section is crossed for super-large-diameter shield
CN111079342A (en) * 2019-11-29 2020-04-28 中铁工程装备集团有限公司 TBM tunneling performance prediction method based on online rock mass grade classification

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104732059A (en) * 2015-01-12 2015-06-24 天津大学 Method for calculating total thrust in hard rock TBM device tunneling process
CN108241780A (en) * 2017-12-29 2018-07-03 天津大学 Composite shield tunnels the computational methods of cutter head torque in ground mixes geology
CN110362899A (en) * 2019-07-01 2019-10-22 中铁隧道局集团有限公司 The cutter head torque calculation method of basement rock protrusion section is crossed for super-large-diameter shield
CN111079342A (en) * 2019-11-29 2020-04-28 中铁工程装备集团有限公司 TBM tunneling performance prediction method based on online rock mass grade classification

Non-Patent Citations (5)

* Cited by examiner, † Cited by third party
Title
A discussion on hard rock TBM cutter wear and cutterhead intervention interval length evaluation;EbrahimFarrokh等;《Tunnelling and Underground Space Technology》;20181130;第81卷;第336-357页 *
Disc cutter wear prediction for a hard rock TBM cutterhead based on energy analysis;LihuiWang等;《Tunnelling and Underground Space Technology》;20150830;第50卷;第324-333页 *
TBM刀盘与岩石相对刚度对盘形滚刀受力的影响分析;宋克志等;《应用基础与工程科学学报》;20110830;第19卷(第4期);第591-598页 *
TBM刀盘推力与扭矩预测方法分析;曹建锋等;《建筑机械化》;20180515;第51-54页 *
考虑回填层的护盾式TBM隧道结构设计方法研究;吴圣智等;《岩土工程学报》;20180530;第40卷(第5期);第857-863页 *

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