CN103419089A - Complete machine working performance optimum design method for circular sawing machine - Google Patents
Complete machine working performance optimum design method for circular sawing machine Download PDFInfo
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Abstract
The invention discloses a complete machine working performance optimum design method for a circular sawing machine. The complete machine working performance optimum design method for the circular sawing machine comprises the following steps of (1) using an LMS vibration noise testing system and the hammer test method to measure to obtain the natural frequency of a circular saw blade and modal frequencies of main components of the circular sawing machine, (2) carrying out measurement to obtain working modal frequencies of main components of the circular sawing machine on the sawing working condition, carrying out aggregation on the modal frequencies of the circular sawing machine on the sawing working condition and modal frequencies of the circular sawing machine in a hammer test to obtain the resonance band frequency of the circular sawing machine, and (3) obtaining the sawing tooth frequency according to the number of teeth of the circular saw blade and the rotating speed in a calculation mode. Due to the fact that the sawing tooth frequency is kept away from the resonance band frequency of the circular sawing machine and the natural frequency of the circular saw blade, the purpose of reducing vibration and noise and the purpose of improving complete machine performance are achieved. The complete machine working performance optimum design method for the circular sawing machine uses the dynamic performance of the circular sawing machine as an evaluation objective, uses the LMS testing system as experiment measures, uses sawing machining parameters as optimization objects, and has the advantages of being clear in target, convenient to analyze, rapid in analysis and the like.
Description
Technical field
Patent design Machine Tool design of the present invention field, relate in particular to a kind of circular saw bench complete machine dynamic duty Design of Performance method.
Background technology
Circular saw bench is widely used in the metal material patch blanking, has the advantages such as high stock-removing efficiency and high cutting precision.The workpiece of sawing different materials, and, under the requirement of different cutting-rates, the machined parameters of sawing machine always will be constantly updated variation.But because unavoidable sawing tooth in the architectural characteristic of sawing machine own and sawing process waits impact frequently, make sawing machine produce larger vibration and noise, affect the processing characteristics of lathe.Therefore, how to choose suitable machined parameters and guarantee that in sawing process, machine vibration is little, noise is low, significant.Can the quality of the dynamic property of machine tool structure has directly affected the machine tool structure system meet high accuracy, high stability, high efficiency processing request.The vibration-testing of machine tool structure system is very important dynamic performance testing content, and vibration-testing can reproduce truly, fully and disclose affects the Structural Dynamics of the actual process of lathe essence.
Summary of the invention
Technical scheme of the present invention is:
Step a, use LMS vibration and noise test system, by the Hammering Test method, the natural mode of vibration of saw blade tested, and obtains the model frequency of saw blade;
Step b, use LMS vibration and noise test system, by the Hammering Test method, each critical piece of sawing machine carried out to the mode test, obtains the intrinsic modal parameters of machine tool system, obtains the model frequency of each critical piece of sawing machine;
Step c, carry out at sawing machine under the operating mode of sawing processing, the operation mode of each critical piece of test lathe, the operation mode frequency of acquisition lathe.And the model frequency of lathe under Hammering Test and under the sawing operating mode is carried out to Macro or mass analysis, obtain the resonant belt frequency of sawing machine;
Steps d, calculate the sawing tooth frequently according to the saw blade number of teeth and rotating speed.Allow the sawing tooth frequently avoid the resonant belt frequency of lathe and the intrinsic frequency of saw blade, thereby reach the purpose of vibration and noise reducing, raising complete machine tool dynamic property.
Further, described step a further comprises: while by the Hammering Test method, the natural mode of vibration of saw blade being tested, the mounting means of saw blade is original support, by standard, is arranged on the saw girff.Because test environment is more severe, select the locomotivity hammer, the test mode of fixation of sensor.
Further, described step b further comprises: in the test of circular saw bench complete machine natural mode of vibration, the layout of measuring point makes its mean allocation on each parts as far as possible, in the position, joint portion of paying close attention to, can suitably increase measuring point, and makes it avoid the mode node.Be illustrated for example, as shown in Figure 3, according to the practical structures of certain circular saw bench, set up whole measuring point position.As shown in Figure 4, column, transmission case and saw blade carry out the measuring point modeling of local refinement.
Further, described step c further comprises: under the sawing operating mode during mode of test lathe each critical piece, its measuring point choose in arrangement and step b to choose mode similar, be also the position, junction that each parts of lathe are selected in requirement as far as possible.
Further, described steps d further comprises: when saw blade incision workpiece, owing to being subject to the reason such as frictional resistance, the actual speed of saw blade descends a little, while causing the sawing tooth frequently to compare idle running, some hysteresis errors are arranged, this error amount is about between 1%～3%.
Further, described steps d further comprises: due to reasons such as Machine Tool design requirements, the sawing tooth of saw blade belongs to low-frequency range frequently.Because the model frequency scope of sawing machine and saw blade is generally wider, the sawing tooth frequently must be avoided its 1/2 frequency multiplication, 1/3 octave component, 1/4 frequency multiplication simultaneously again ... Deng.
The accompanying drawing explanation
Fig. 1 is the flow chart of circular saw bench complete machine dynamic duty Design of Performance method of the present invention;
Fig. 2 is certain circular sawing machine complete machine simplified model;
Fig. 3 is structured testing modeling schematic diagram;
Fig. 4 is local measuring point modeling schematic diagram;
The specific embodiment
In order to make the purpose, technical solutions and advantages of the present invention clearer, below in conjunction with accompanying drawing and example, the present invention is further elaborated.Should illustrate, instantiation described herein only, for explaining the present invention, is not intended to limit the present invention.
The sawing machine machined parameters mainly comprises saw blade rotating speed and saw blade horizontal feed speed, the frequency characteristic of saw blade influence of rotation speed exciting force, and feed speed affects the size of exciting force.Here the influences vibration frequency, therefore pay close attention to this machined parameters of saw blade rotating speed.
Calculated the sawing tooth frequency of saw blade by saw blade rotating speed and the saw blade number of teeth, the sawing tooth belongs to the external drive frequency frequently concerning lathe, the core of the inventive method is exactly to allow the sawing tooth frequently avoid the resonant belt frequency of lathe and the intrinsic frequency of saw blade, thereby reaches the purpose of vibration and noise reducing, raising complete machine tool dynamic property.
Shown in Fig. 1, circular saw bench complete machine dynamic duty Design of Performance method provided by the invention specifically comprises following step:
Step 13, carry out at sawing machine under the operating mode of sawing processing, the operation mode of each critical piece of test lathe, the operation mode frequency of acquisition lathe.And the model frequency of lathe under Hammering Test and under the sawing operating mode is carried out to Macro or mass analysis, obtain the resonant belt frequency of sawing machine;
Below take certain hard alloy circular sawing machine sawing round steel workpiece is preferred embodiment, and above-mentioned steps of the present invention is carried out to further illustrated in greater detail.As shown in Figure 2, two columns in left and right are arranged on sawing machine, by the left and right vice blade of a sword on work stage and column, carry out clamping work pieces, workpiece maintains static; Saw blade is arranged on transmission case, and the movement by transmission case on guide rail drives saw blade and does feed motion.Therefore, under the sawing operating mode, due to the incentive action of the factors such as sawing tooth frequency, can make to saw girff and vibration occur in running, rock, and then cause vibration and the noise of complete machine.
The sawing machine structure of analysis chart 2 is known, and the main mode of sawing machine lathe bed roughly can be divided into two parts: the one, and column and pedestal are at the mode at place, joint portion, the 2nd, the torsion mode of transmission case and guiding rail joint portion.The mode at its central post and pedestal fixing combination portion place can obtain by the Excitation and response of test column surface X and Z direction, and the torsion mode of transmission case and guide rail faying face can obtain by the Excitation and response of test transmission case surface Z direction.To sum up, the mode of sawing machine lathe bed test is divided into to column and two parts of transmission case carry out.The process that circular saw bench complete machine dynamic duty Design of Performance method provided by the invention is applied in certain circular saw bench is as follows:
Steps A, carry out the mode test by the Hammering Test method to sintered carbide circular saw.Use the vibration and noise test system of LMS (LMS INTERNATIONAL) company, adopt the Hammering Test method to carry out the mode test to saw blade.For each measuring point, firmly hammer repeats to knock 5 times, guarantees at same position, and is that same person is taken the operation of exciting hammer always in guarantee test.The mounting means of saw blade is original support, by standard, is arranged on the saw girff.Because test environment is more severe, select the locomotivity hammer, the test mode of fixation of sensor.It is f that test result obtains the saw blade intrinsic frequency
1=(31.092Hz, 39.575Hz, 49.509Hz, 65.847Hz, 125.462Hz).
Step B, carry out the mode test by the Hammering Test method to column and two critical pieces of transmission case of sawing machine.As shown in Figure 3 and Figure 4, use the Geometry module of LMS software to set up the geometrical test model, test obtains the model frequency of sawing machine critical piece.
Step C, the operation mode of test sawing machine column and transmission case.At sawing machine, carry out under the operating mode of sawing processing, test obtains column and transmission case operation mode frequency.And the model frequency of lathe under Hammering Test and under the sawing operating mode is gathered, obtaining column directions X resonant belt and mainly concentrate on 99Hz～114Hz, the frequency response amplitude reaches 0.01g/N; The main resonant belt of column Z direction concentrates on 36Hz～38.5Hz, 131～138Hz, and its frequency response amplitude reaches 0.03g/N; The resonant belt of transmission case concentrates on 223～226Hz, and the frequency response amplitude reaches 0.01g/N.The resonant belt that is sawing machine is f
2=(36Hz～38.5Hz, 99Hz～114Hz, 131Hz～138Hz, 223Hz～226Hz).
Step D, the optimal design of machined parameters.The sintered carbide circular saw that this example adopts has 60 teeth, and according to the Machine Tool design requirement, the range of speeds that saw blade can be realized is 30～50r/min, and calculating the sawing tooth is 30～50Hz frequently.Suppose that the sawing tooth is f frequently, consider the hysteresis error of sawing rotating speed with respect to sawing tooth frequency 1Hz left and right, f=(29～49Hz).Based on sawing tooth frequency, f must avoid saw blade intrinsic frequency f
1Resonant belt f with sawing machine
2Thoughts on Optimized Design, can obtain f ≠ f
1/ n and f ≠ f
2/ n (n=1,2,3,4...),
Solve: f=(29) ∪ (32) ∪ (38,39) ∪ (41) ∪ (43,44) ∪ (47,48)
Add the hysteresis of sawing rotating speed with respect to sawing frequency 1Hz left and right, the feasible sawing rotating speed after being optimized:
n′＝(30)∪(33)∪(39，40)∪(42)∪(44，45)∪(48，49)(r/min)
In sum, as saw blade selection of speed n '=(30) ∪ (33) ∪ (39,40) ∪ (42) ∪ (44,45) ∪ (48,49) (r/min) time, can reduce vibration, reduce Cutting noise, improve sawing machine complete machine dynamic duty performance.、
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, for example the present invention not only is confined to be applied in hard alloy circular sawing machine, can also be applied to the lathe of other types.All any modifications of doing within the spirit and principles in the present invention, be equal to and replace and improvement etc., within all should being included in protection scope of the present invention.
Claims (6)
1. a circular saw bench complete machine dynamic duty Design of Performance method is characterized in that comprising the following steps:
Step a, use LMS vibration and noise test system, by the Hammering Test method, the natural mode of vibration of saw blade tested, and obtains the model frequency of saw blade;
Step b, use LMS vibration and noise test system, by the Hammering Test method, each critical piece of sawing machine carried out to the mode test, obtains the intrinsic modal parameters of machine tool system, obtains the model frequency of each critical piece of sawing machine;
Step c, carry out at sawing machine under the operating mode of sawing processing, the operation mode of each critical piece of test lathe, the operation mode frequency of acquisition lathe.And the model frequency of lathe under Hammering Test and under the sawing operating mode is carried out to Macro or mass analysis, obtain the resonant belt frequency of sawing machine;
Steps d, calculate the sawing tooth frequently according to the saw blade number of teeth and rotating speed.Allow the sawing tooth frequently avoid the resonant belt frequency of lathe and the intrinsic frequency of saw blade, thereby reach the purpose of vibration and noise reducing, raising complete machine tool dynamic property.
2. circular saw bench complete machine dynamic duty Design of Performance method according to claim 1, it is characterized in that, described step a further comprises: while by the Hammering Test method, the natural mode of vibration of saw blade being tested, the mounting means of saw blade is original support, by standard, is arranged on the saw girff.Because test environment is more severe, select the locomotivity hammer, the test mode of fixation of sensor.According to Figure of description 2, the structure of circular saw bench comprises: 1-lathe bed, 2-guide rail, 3-saw girff, 4-cutterhead, the 5-left and right vice blade of a sword, 6-left and right pillar, 7-workpiece, 8-column case.
3. circular saw bench complete machine dynamic duty Design of Performance method according to claim 1, it is characterized in that, described step b further comprises: in the test of circular saw bench complete machine natural mode of vibration, the layout of measuring point makes its mean allocation on each parts as far as possible, can suitably increase measuring point in the position, joint portion of paying close attention to, and make it avoid the mode node.
4. circular saw bench complete machine dynamic duty Design of Performance method according to claim 1, it is characterized in that, described step c further comprises: while testing the mode of each critical piece of lathe under the sawing operating mode, its measuring point choose in arrangement and step b to choose mode similar, require to select the position, junction of each parts of lathe as far as possible.
5. circular saw bench complete machine dynamic duty Design of Performance method according to claim 1, it is characterized in that, described steps d further comprises: when saw blade incision workpiece, owing to being subject to the reasons such as frictional resistance, the actual speed of saw blade descends a little, while causing the sawing tooth frequently to compare idle running, some hysteresis errors are arranged, this error amount is about between 1%～3%.
6. circular saw bench complete machine dynamic duty Design of Performance method according to claim 1, is characterized in that, described steps d further comprises: due to reasons such as Machine Tool design requirements, the sawing tooth of saw blade belongs to low-frequency range frequently.Because the model frequency scope of sawing machine and saw blade is generally wider, the sawing tooth frequently must be avoided its 1/2 frequency multiplication, 1/3 octave component, 1/4 frequency multiplication simultaneously again ... Deng.
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103629295A (en) * | 2013-12-05 | 2014-03-12 | 中冶东方工程技术有限公司 | Disk saw blade damping device |
| CN107238480A (en) * | 2017-06-20 | 2017-10-10 | 西北工业大学 | Milling process damping scaling method based on operational modal analysis |
| CN109142535A (en) * | 2018-04-08 | 2019-01-04 | 哈尔滨理工大学 | A kind of saw blade non-destructive testing device based on acoustic resonance spectrum |
| CN109202536A (en) * | 2018-11-02 | 2019-01-15 | 浙江工业大学 | Circular saw bench saw blade single vibration test macro |
| CN109202537A (en) * | 2018-11-02 | 2019-01-15 | 浙江工业大学 | A kind of circular saw bench guide rail vibration test system |
| CN109238435A (en) * | 2018-11-02 | 2019-01-18 | 浙江工业大学 | A kind of circular saw bench gear-box vibration test system |
| CN109514000A (en) * | 2018-11-02 | 2019-03-26 | 浙江工业大学 | Circular saw bench noise measuring system |
| CN117808798A (en) * | 2024-02-29 | 2024-04-02 | 山东万利精密机械制造有限公司 | Visual acquisition and analysis method for intelligent manufacturing production data of circular sawing machine |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103629295A (en) * | 2013-12-05 | 2014-03-12 | 中冶东方工程技术有限公司 | Disk saw blade damping device |
| CN107238480A (en) * | 2017-06-20 | 2017-10-10 | 西北工业大学 | Milling process damping scaling method based on operational modal analysis |
| CN109142535A (en) * | 2018-04-08 | 2019-01-04 | 哈尔滨理工大学 | A kind of saw blade non-destructive testing device based on acoustic resonance spectrum |
| CN109202536A (en) * | 2018-11-02 | 2019-01-15 | 浙江工业大学 | Circular saw bench saw blade single vibration test macro |
| CN109202537A (en) * | 2018-11-02 | 2019-01-15 | 浙江工业大学 | A kind of circular saw bench guide rail vibration test system |
| CN109238435A (en) * | 2018-11-02 | 2019-01-18 | 浙江工业大学 | A kind of circular saw bench gear-box vibration test system |
| CN109514000A (en) * | 2018-11-02 | 2019-03-26 | 浙江工业大学 | Circular saw bench noise measuring system |
| CN117808798A (en) * | 2024-02-29 | 2024-04-02 | 山东万利精密机械制造有限公司 | Visual acquisition and analysis method for intelligent manufacturing production data of circular sawing machine |
| CN117808798B (en) * | 2024-02-29 | 2024-05-14 | 山东万利精密机械制造有限公司 | Visual acquisition and analysis method for intelligent manufacturing production data of circular sawing machine |
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