CN116127640A - Crane structural parameter stress analysis method - Google Patents

Crane structural parameter stress analysis method Download PDF

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Publication number
CN116127640A
CN116127640A CN202310050732.0A CN202310050732A CN116127640A CN 116127640 A CN116127640 A CN 116127640A CN 202310050732 A CN202310050732 A CN 202310050732A CN 116127640 A CN116127640 A CN 116127640A
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crane
follows
analysis method
calculation formula
structural parameter
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Inventor
路强
朱仪
高军武
潘磊
孙鸿
谢绍南
姚克海
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Jiangsu Sugang Intelligent Equipment Industry Innovation Center Co ltd
Nanjing Port Machinery & Heavy Industry Manufacture Co ltd
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Jiangsu Sugang Intelligent Equipment Industry Innovation Center Co ltd
Nanjing Port Machinery & Heavy Industry Manufacture Co ltd
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    • 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
    • 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 discloses a crane structure parameter stress analysis method, which belongs to the technical field of mechanical design and manufacture, and comprises the steps of selecting a crane type, inputting parameter data of each structure of a crane, establishing a three-dimensional model of each structure of the crane according to the input parameter data, assembling the three-dimensional model of each structure of the crane to generate a crane integral three-dimensional model, carrying out optimization calculation on the crane model, calculating stress data of the crane model according to the parameter data, judging whether the calculated stress data is in accordance with a use standard or not, and avoiding the possibility of damage, collapse and transmission caused by model design problems in a model design stage.

Description

Crane structural parameter stress analysis method
Technical Field
The invention belongs to the technical field of mechanical design and manufacture, and particularly relates to a stress analysis method for structural parameters of a crane.
Background
At present, with the rapid development of modern science and technology, the scale of industrial production is enlarged and the degree of automation is improved, the crane is used as large lifting equipment, the crane which bears very heavy work tasks in daily work is increasingly widely applied in the modern production process, the effect is increasingly larger, and the requirement on the crane is also increasingly higher. The characteristics and development trend of modern cranes are particularly represented in the following aspects: the key products are large-sized; modularization of serial products; the general product is miniaturized and light; product performance is automated; combining and unitizing products; microcomputer-based product design; product structure is new; the product manufacture is flexible.
The crane manufacturing industry in China starts in the 50 th century, and the crane design in the stage is mostly introduced from the soviet union, so that the early crane steel structure design theory is deviated from conservation, and is mainly characterized by high safety coefficient and great structural self-weight, so that the whole size and weight of the crane are huge artificially. Modularized, parametric design and simulation analysis technologies have not been fully popularized and applied in the crane industry.
If the crane modeling is not standard, the crane is damaged when light during construction or use, and the crane structure collapses when heavy, which are all unwilling to see during construction and repair. In order to avoid the above-mentioned accidents during the construction or repair of the crane, after the modeling design of the crane is completed, an analysis of the stress situation of the already designed crane model is required.
Disclosure of Invention
Problems to be solved
Aiming at the problem that if modeling of the existing crane is not standard, the crane is damaged when the crane is light in the building or using process, and the crane structure collapses when the crane is heavy, the invention provides a crane structure parameter stress analysis method.
Technical proposal
In order to solve the problems, the invention adopts the following technical scheme.
A method for analyzing structural parameter stress of a crane comprises the following steps:
step 1: selecting a crane type and inputting parameter data of each structure of the crane;
step 2: establishing a three-dimensional model of each structure of the crane according to the input parameter data;
step 3: assembling the three-dimensional model of each structure of the crane to generate a crane integral three-dimensional model;
step 4: carrying out optimization calculation on the crane model, and calculating according to the parameter data to obtain stress data of the crane model;
step 5: and judging whether the crane model accords with the use standard or not by using the calculated stress data.
Preferably, the leg pressure calculation formula is as follows:
Figure SMS_1
wherein G is Z Is the dead weight of the whole machine, k Q Q is a lifting dynamic planting coefficient, b is a base distance, and l is a track distance.
Preferably, the formula for calculating the throwing hook is as follows:
Figure SMS_2
Figure SMS_3
wherein Q0 and Q are the dead weight of the lifting appliance, eta is the mechanism group effect, eta s To raise pulley block effect eta d Is a pulley block effect.
Further, the calculation formula of the double rope throwing grab bucket is as follows:
Figure SMS_4
further, the calculation formula of the four-rope throwing grab bucket is as follows:
Figure SMS_5
further, wherein eta s The calculation formula of (2) is as follows:
Figure SMS_6
wherein eta 0 For single pulley efficiency, η when applied to roller bearings 0 =0.98, η when for plain bearings 0 Further, the calculation formula for the single-linked reel and the double-linked reel is as follows:
Figure SMS_7
Figure SMS_8
M W2 ＝S max D 0
Figure SMS_9
Figure SMS_10
Figure SMS_11
wherein delta y Delta as the actual applied pressure h To actually synthesize the pressure, k W For the actual stability coefficient, D is the diameter of the bottom of the drum groove, D 0 For the nominal diameter of the drum, delta is the wall thickness of the drum, P is the pitch of the rope grooves, A 1 For the roll stress reduction factor, A 2 For multi-layer winding factor, M W1 Is a single-link winding drum M W2 Is a duplex winding drum.
Further, the high-speed shaft coupling moment Mj is calculated as follows:
Figure SMS_12
wherein Pe is the rated power of the motor, ne is the rated rotation speed of the motor, lambda m Kg is a calculation coefficient, K3 is an angle deviation coefficient, and K1 is a coupling importance coefficient.
Still further, the brake safety factor Kz is calculated as follows:
Figure SMS_13
wherein m is the multiplying power of the pulley block, and i is the transmission ratio of the speed reducer.
Still further, the recommended braking time calculation formula is as follows:
Figure SMS_14
Figure SMS_15
wherein J is e J is the moment of inertia of the brake and the coupling d The moment of inertia of the motor is given, and J is the total moment of inertia.
According to the crane structure parameter stress analysis method, the crane type is selected, parameter data of each structure of a crane are input, a three-dimensional model of each structure of the crane is built according to the input parameter data, the three-dimensional model of each structure of the crane is assembled to generate an integral three-dimensional model of the crane, the crane model is optimized and calculated, stress data of the crane model are obtained according to the parameter data, the calculated stress data are used for judging, whether the crane model meets the use standard or not is judged, and the possibility of damage collapse transmission caused by model design problems is avoided in the model design stage.
Advantageous effects
Compared with the prior art, the invention has the beneficial effects that:
(1) According to the invention, the three-dimensional model of each structure of the crane is built according to the input parameter data, the three-dimensional model of each structure of the crane is assembled to generate the integral three-dimensional model of the crane, the crane model is optimally calculated, the stress data of the crane model is obtained according to the parameter data, whether the generated crane model meets the specification can be calculated and judged, and the possibility of damage, collapse and transmission caused by the model design problem is avoided in the model design stage;
(2) According to the invention, stress calculation is carried out on the arm support, the trunk bridge, the large pull rod, the turntable, the herringbone frame, the balance beam, the small pull rod, the rack box body structure, the front girder, the rear girder, the door leg, the lower cross beam and the trapezoid frame structure, so that the stress condition of each structure of the crane can be known in detail, and whether the modeling standard is met or not can be judged;
(3) After all data are determined, the data can be stored in the form of project files, all the data can be determined by opening the project files when the data are used next time, new projects can be generated after partial data are modified on the basis of the data, a large amount of modeling and stress analysis calculation time is saved, and the working efficiency is improved.
Drawings
In order to more clearly illustrate the technical solutions in embodiments or examples of the present application, the drawings that are required for use in the embodiments or examples description will be briefly described below, and it is apparent that the drawings in the following description are only some embodiments of the present application and therefore should not be construed as limiting the scope, and that other drawings may be obtained according to the drawings without inventive effort to those of ordinary skill in the art.
FIG. 1 is a schematic diagram of the steps of the present invention;
FIG. 2 is a schematic diagram of four-bar point optimization parameter input according to the present invention;
FIG. 3 is a diagram of a four-bar optimization process and results of the present invention;
FIG. 4 is a schematic diagram of the four-bar linkage optimization result preservation of the present invention;
FIG. 5 is a schematic diagram of four-bar linkage optimization parameter adjustment according to the present invention;
FIG. 6 is a schematic diagram of a four-bar optimized displacement list of the present invention;
FIG. 7 is a schematic diagram of a four bar linkage displacement graph according to the present invention;
FIG. 8 is a schematic diagram of a balance weight optimization calculation parameter input interface of the present invention;
FIG. 9 is a column of displacements of the balance weight optimization system of the present invention with moments representing intent;
FIG. 10 is a schematic diagram of a comprehensive moment diagram of a balance weight optimization system of the present invention;
FIG. 11 is a schematic diagram of an overall stability base parameter input interface of the present invention;
FIG. 12 is a schematic diagram of a parameter interface of the overall stability boom balancing system of the present invention;
FIG. 13 is a schematic diagram of a general overall machine centroid parameter interface in accordance with the present invention;
FIG. 14 is a schematic view of the overall machine windward parameter interface of the present invention;
FIG. 15 is a schematic diagram of the overall stability calculation of the present invention;
FIG. 16 is a schematic illustration of a wheel pressure calculation interface in accordance with the present invention;
FIG. 17 is a graph showing the results of wheel pressure calculations according to the present invention;
FIG. 18 is a schematic diagram of a mechanism selection interface of the present invention;
FIG. 19 is a schematic view of a hoisting mechanism-wire rope selection interface of the present invention;
FIG. 20 is a schematic view of an interface for checking the distance between a hoisting mechanism and a brake, and a hook sliding distance according to the present invention.
Detailed Description
For the purposes of making the objects, technical solutions and advantages of the embodiments of the present application more apparent, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments, and that the components of the embodiments of the present application generally described and illustrated in the drawings herein may be arranged and designed in various different configurations.
Thus, the following detailed description of the embodiments of the present application, provided in the accompanying drawings, is not intended to limit the scope of the application as claimed, but is merely representative of selected embodiments of the application, based on which all other embodiments that may be obtained by one of ordinary skill in the art without making inventive efforts are within the scope of this application.
Example 1
As shown in fig. 1, a crane structural parameter stress analysis method mainly comprises the following steps: selecting a crane type, inputting parameter data of each structure of the crane, establishing a three-dimensional model of each structure of the crane according to the input parameter data, assembling the three-dimensional models of each structure of the crane to generate an integral three-dimensional model of the crane, carrying out optimization calculation on the crane model, calculating stress data of the crane model according to the parameter data, judging by using the calculated stress data, and judging whether the crane model accords with a use standard.
The leg pressure calculation formula in the optimization calculation is as follows:
Figure SMS_16
Figure SMS_17
wherein G is Z Is the dead weight of the whole machine, k Q Q is a lifting dynamic planting coefficient, b is a base distance, and l is a track distance.
The calculation formula of the throwing hook is as follows:
Figure SMS_18
Figure SMS_19
wherein Q0 and Q are the dead weight of the lifting appliance, eta is the mechanism group effect, eta s To raise pulley block effect eta d Is a pulley block effect.
The calculation formula of the double rope throwing grab bucket is as follows:
Figure SMS_20
the calculation formula of the four-rope throwing grab bucket is as follows:
Figure SMS_21
wherein eta s The calculation formula of (2) is as follows:
Figure SMS_22
wherein eta 0 For single pulley efficiency, η when applied to roller bearings 0 =0.98, η when for plain bearings 0 The calculation formula for the single-link reel and the double-link reel=0.96 is as follows:
Figure SMS_23
Figure SMS_24
M W2 ＝S max D 0
Figure SMS_25
Figure SMS_26
Figure SMS_27
wherein delta y Delta as the actual applied pressure h To actually synthesize the pressure, k W For the actual stability coefficient, D is the diameter of the bottom of the drum groove, D 0 For the nominal diameter of the drum, delta is the wall thickness of the drum, P is the pitch of the rope grooves, A 1 For the roll stress reduction factor, A 2 For multi-layer winding factor, M W1 Is a single-link winding drum M W2 Is a duplex winding drum.
The calculation formula of the high-speed shaft coupling moment Mj is as follows:
Figure SMS_28
wherein Pe is the rated power of the motor, ne is the rated rotation speed of the motor, lambda m Kg is a calculation coefficient, K3 is an angle deviation coefficient, and K1 is a coupling importance coefficient.
The calculation formula of the brake safety coefficient Kz is as follows:
Figure SMS_29
wherein m is the multiplying power of the pulley block, and i is the transmission ratio of the speed reducer.
The recommended braking time calculation formula is as follows:
Figure SMS_30
Figure SMS_31
wherein J is e J is the moment of inertia of the brake and the coupling d The moment of inertia of the motor is given, and J is the total moment of inertia.
As can be seen from the above description, in this example, by selecting a crane type, inputting parameter data of each structure of the crane, establishing a three-dimensional model of each structure of the crane according to the input parameter data, assembling the three-dimensional model of each structure of the crane, generating an overall three-dimensional model of the crane, performing optimization calculation on the crane model, calculating stress data of the crane model according to the parameter data, and determining whether the crane model meets the use standard by using the calculated stress data.
Example 2
Selecting a crane structure through a visual interface, inputting corresponding specification and model data, displaying a preview graph of the selected crane structure on an interactive interface, automatically updating the preview graph along with the change of the data, dynamically reflecting the real structure of a product, calculating the input data, calling the corresponding data from a product database to be displayed in the interface for a designer to use, generating a two-dimensional engineering drawing and a three-dimensional model of the selected crane structure, assembling and assembling the three-dimensional model according to the selected crane type, generating a whole three-dimensional model of the crane, and storing all the data in the form of project files after all the data are input and confirmed. And carrying out optimization calculation on the crane model, calculating according to the parameter data to obtain stress data of the crane model, and judging whether the crane model accords with the use standard or not by using the calculated stress data.
The leg pressure calculation formula in the optimization calculation is as follows:
Figure SMS_32
Figure SMS_33
wherein G is Z Is the dead weight of the whole machine, k Q Q is a lifting dynamic planting coefficient, b is a base distance, and l is a track distance.
The calculation formula of the throwing hook is as follows:
Figure SMS_34
Figure SMS_35
wherein Q0 and Q are the dead weight of the lifting appliance, eta is the mechanism group effect, eta s To raise pulley block effect eta d Is a pulley block effect.
The calculation formula of the double rope throwing grab bucket is as follows:
Figure SMS_36
the calculation formula of the four-rope throwing grab bucket is as follows:
Figure SMS_37
wherein eta s The calculation formula of (2) is as follows:
Figure SMS_38
wherein eta 0 For single pulley efficiency, η when applied to roller bearings 0 =0.98, η when for plain bearings 0 The calculation formula for the single-link reel and the double-link reel=0.96 is as follows:
Figure SMS_39
Figure SMS_40
M W2 ＝S max D 0
Figure SMS_41
Figure SMS_42
Figure SMS_43
wherein delta y Delta as the actual applied pressure h To actually synthesize the pressure, k W For the actual stability coefficient, D is the diameter of the bottom of the drum groove, D 0 For the nominal diameter of the drum, delta is the wall thickness of the drum, P is the pitch of the rope grooves, A 1 For the roll stress reduction factor, A 2 For multi-layer winding factor, M W1 Is a single-link winding drum M W2 Is a duplex winding drum.
The calculation formula of the high-speed shaft coupling moment Mj is as follows:
Figure SMS_44
wherein Pe is the rated power of the motor, ne is the rated rotation speed of the motor, lambda m Kg is a calculation coefficient, K3 is an angle deviation coefficient, and K1 is a coupling importance coefficient.
The calculation formula of the brake safety coefficient Kz is as follows:
Figure SMS_45
wherein m is the multiplying power of the pulley block, and i is the transmission ratio of the speed reducer.
The recommended braking time calculation formula is as follows:
Figure SMS_46
Figure SMS_47
wherein J is e J is the moment of inertia of the brake and the coupling d The moment of inertia of the motor is given, and J is the total moment of inertia.
Example 2
First, in the four-bar interface, a single click of "geometry optimization/parameter input/user input" enters the parameter input dialog. The dialog box is used for inputting each parameter of the geometric dimension of the four-bar combined arm support system, inputting the upper and lower bounds of the geometric dimension parameter, and calculating the four-bar dimension parameter. As shown in fig. 2.
Optimizing calculation and results: "run" control: clicking the control to perform optimization calculation. "abort optimization" control: this control may be terminated by clicking on it as long as it is available at the time of the optimization calculation. As shown in fig. 3.
"save" control: the results of the optimization are stored in a database (the data to be saved requires entry of item numbers and personnel names). As shown in fig. 4.
Adjusting parameter control: and (3) rounding calculation is carried out on the result of the optimization calculation, and the accuracy of the rounding calculation is determined by setting parameters/decimal places. Shown in fig. 5.
The optimized result query is mainly used for parameter values after program optimization is finished. The interface of the four-bar linkage displacement list and the four-bar linkage displacement curve graph can be checked with the optimization result of geometry optimization/initial parameter result query. As shown in fig. 6 and 7.
Clicking 'dead weight optimization/parameter input/user input' on the balance weight optimization calculation parameter input interface enters a geometric dimension parameter input dialog box. As shown in fig. 8, the steps are as above, the balance weight optimizing system displacement column, and the moment table results and moment curve results are as shown in fig. 9 and 10.
The overall stability calculation operation steps are similar to those described above, and the operation interfaces are shown in fig. 11 to 15.
The wheel pressure calculation and results are shown in fig. 16 and 17.
The institution model selection calculation is shown in fig. 18-20.
The foregoing examples have shown only the preferred embodiments of the invention, which are described in more detail and are not to be construed as limiting the scope of the invention. It should be noted that modifications, improvements and substitutions can be made by those skilled in the art without departing from the spirit of the invention, which are all within the scope of the invention.

Claims (10)

1. The method for analyzing the structural parameter stress of the crane is characterized by comprising the following steps of:
step 1: selecting a crane type and inputting parameter data of each structure of the crane;
step 2: establishing a three-dimensional model of each structure of the crane according to the input parameter data;
step 3: assembling the three-dimensional model of each structure of the crane to generate a crane integral three-dimensional model;
step 4: carrying out optimization calculation on the crane model, and calculating according to the parameter data to obtain stress data of the crane model;
step 5: and judging whether the crane model accords with the use standard or not by using the calculated stress data.
2. The crane structural parameter stress analysis method according to claim 1, wherein: the leg pressure calculation formula in the optimization calculation is as follows:
Figure QLYQS_1
Figure QLYQS_2
wherein G is Z Is the dead weight of the whole machine, k Q Q is a lifting dynamic planting coefficient, b is a base distance, and l is a track distance.
3. The crane structural parameter stress analysis method according to claim 2, wherein: the calculation formula of the throwing hook is as follows:
Figure QLYQS_3
Figure QLYQS_4
wherein Q0 and Q are the dead weight of the lifting appliance, eta is the mechanism group effect, eta s To raise pulley block effect eta d Is a pulley block effect.
4. A crane structural parameter stress analysis method according to claim 3, wherein: the calculation formula of the double rope throwing grab bucket is as follows:
Figure QLYQS_5
5. the crane structural parameter stress analysis method according to claim 4, wherein: the calculation formula of the four-rope throwing grab bucket is as follows:
Figure QLYQS_6
6. a crane structural parameter stress as claimed in claim 5An analytical method characterized by: wherein eta s The calculation formula of (2) is as follows:
Figure QLYQS_7
wherein eta 0 For single pulley efficiency, η when applied to roller bearings 0 =0.98, η when for plain bearings 0 ＝0.96。
7. The crane structural parameter stress analysis method according to claim 6, wherein: the calculation formulas for the single-link winding drum and the double-link winding drum are as follows:
Figure QLYQS_8
/>
Figure QLYQS_9
M W2 ＝S max D 0
Figure QLYQS_10
Figure QLYQS_11
Figure QLYQS_12
wherein delta y Delta as the actual applied pressure h To actually synthesize the pressure, k W For the actual stability coefficient, D is the diameter of the bottom of the drum groove, D 0 For the nominal diameter of the drum, delta is the wall thickness of the drum, P is the pitch of the rope grooves, A 1 For the roll stress reduction factor, A 2 Is wound in multiple layersCoefficient M W1 Is a single-link winding drum M W2 Is a duplex winding drum.
8. The crane structural parameter stress analysis method according to claim 7, wherein: the calculation formula of the high-speed shaft coupling moment Mj is as follows:
Figure QLYQS_13
wherein Pe is the rated power of the motor, ne is the rated rotation speed of the motor, lambda m Kg is a calculation coefficient, K3 is an angle deviation coefficient, and K1 is a coupling importance coefficient.
9. The crane structural parameter stress analysis method according to claim 8, wherein: the calculation formula of the brake safety coefficient Kz is as follows:
Figure QLYQS_14
wherein m is the multiplying power of the pulley block, and i is the transmission ratio of the speed reducer.
10. The crane structural parameter stress analysis method according to claim 9, wherein: the recommended braking time calculation formula is as follows:
Figure QLYQS_15
Figure QLYQS_16
wherein J is e J is the moment of inertia of the brake and the coupling d Is the rotational inertia of the motor [ J ]]Is the total moment of inertia.
CN202310050732.0A 2023-02-01 2023-02-01 Crane structural parameter stress analysis method Pending CN116127640A (en)

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