JP6013679B2 - Aqueous polymer damping material and machine tool using the same - Google Patents

Description

  In the present invention, when a damping material of an aqueous solution of a polymer that dampens vibration epochally (hereinafter referred to as a damping material) and the damping material is encapsulated in a timely manner, the vibration generated at the time of cutting coincides with the resonance point. In particular, the present invention relates to a machine tool that enables cutting without deteriorating the cutting conditions by changing the resonance point of the machine body to a place where the cutting conditions are not affected.

Machine tools such as lathes that rotate by cutting a workpiece and milling machines that rotate by cutting a tool depend on the type of tool and the material of the workpiece. Determine cutting conditions. Cutting conditions affect the quality of cutting itself such as dimensional accuracy, shape accuracy, and surface roughness, but also affect tool life and cutting time. Therefore, it is extremely important to find an appropriate cutting condition and perform cutting, particularly in the case of mass production. Of course, in order to maintain the quality of the cutting itself, it is a precondition that the machine tool keeps the amplitude between the tool and the workpiece due to the generated vibration below a certain level during the cutting.

  Here, the specific appropriate cutting condition is a cutting speed corresponding to an appropriate cutting amount and feed speed determined by the tool and the workpiece, and means a relative speed at which the tool and the workpiece surface are in contact with each other. To do. In the case of cutting with a lathe, the spindle speed at which the workpiece is mounted is adjusted according to the diameter of the workpiece, and the cutting speed matches the circumferential tangential speed of the workpiece surface called the peripheral speed. To do.

  However, a machine tool has a plurality of drive sources that generate vibrations, and when the effects of each vibration overlap, a large amplitude called resonance is generated between the workpiece and the tool at a frequency called the resonance frequency. Occurs. When resonance occurs, it affects the quality of the cutting itself, so abandon the appropriate cutting conditions, and in general, cutting conditions such as lowering the spindle speed, changing the feed rate, and reducing the cutting depth. Change the cutting. Resonance basically occurs when the natural frequency determined by the shape, size, material Young's modulus and density, and support method of the elements that make up the structure matches the frequency of the periodic external forcing. . In an actual machine, vibration modes from the first order, second order,..., N order in order of large deformation have respective natural frequencies and are combined in each direction. Depending on the direction and direction, the corresponding resonance state appears. In general, the resonance of cutting by a lathe is caused by the rotation of the spindle motor and the relative external positional relationship between the workpiece and the tool. When it occurs and coincides with each natural frequency in each direction, the amplitude on the workpiece side mounted on the spindle increases or the amplitude on the tool side increases, thereby deteriorating the quality of the workpiece. The natural frequency is proportional to the so-called square root of rigidity and inversely proportional to the square root of density.

  A mechanism has been proposed in which a mass capable of changing the mass is assembled to the rear end of the main shaft on which the workpiece is mounted, and when the resonance occurs, the resonance frequency is changed by changing the mass of the weight (for example, Patent Document 1).

JP 2010-42464 A

  According to such a conventional technique, resonance is avoided by connecting a weight corresponding to a workpiece to be connected to the front end side of the main shaft to the rear end side of the main shaft. However, the use of the weight has a problem that it is impossible to prevent the amplitude from increasing by basically increasing the density to lower the resonance frequency and avoiding resonance.

  The configuration of the first invention according to this application for achieving the above object (referring to the invention according to claim 1, the same applies hereinafter) attenuates the vibration by directly contacting the surface of the part of the machine tool where the vibration is generated. The gist of the present invention is that the damping material is an aqueous solution of a polymer. In addition, the component of a vibration generation part means the component which receives a periodic external forcing force and repeats a periodic deformation.

  The structure of the second invention (referring to the invention according to claim 2, hereinafter the same) comprises a gap provided so as to surround the surface of the component of the vibration generating part, and the damping material of the first invention enclosed in the gap. The gist of the present invention is that the damping material is enclosed in a gap when resonance occurs, and directly contacts the surface of the component to reduce resonance and avoid resonance by reducing the natural frequency.

  In addition, the amount of enclosed attenuation material may be variable.

Here, a detachable reinforcing frame can be attached to the vibration generating portion.

  In addition, you may earth | ground and support with arbitrary three or more support bolts among the four or more support bolts which can be moved up and down attached to the predetermined place of the bottom part.

  According to the configuration of the first invention, a high molecular polymer generally known as a polymer is easily available on the market and is inexpensive, and if an aqueous solution dissolved in water is used as a damping material, there is no conventional polymer. Effective mechanical performance can be obtained. In other words, the damping material in the form of an aqueous solution not only has an epoch-making damping ratio, but also directly contacts the vibrating component surface without any gap, and can quickly attenuate all vibrations on the component surface. Therefore, it has a very effective damping function and can be easily transferred using a pump, thereby improving the mechanical performance. This damping function is considered to be caused by the fact that the high molecular weight polymer is a non-Newtonian fluid having both viscosity and elasticity. The high molecular polymer is a general term for high molecular polymers, and various types have been used for various applications in recent years depending on performance. The polymer used in the present invention is a water-soluble PEO-based (polyethylene oxide), and has a feature that it does not cause environmental pollution even if discarded as it is. However, the polymer used as the damping material is not limited to the PEO polymer.

According to the configuration of the second invention, when resonance occurs under appropriate cutting conditions, the damping material of the first invention is enclosed in the gap of the vibration generation site of the machine tool, and the vibration generation site component of the machine tool is used. By contacting the surface, the machine tool becomes denser and lowers the natural frequency, thus avoiding resonance. In general, when the density is increased and the natural frequency is lowered, the amplitude of the general vibration is increased. However, when such a damping material is enclosed, the amplitude can also be decreased. Therefore, the machine tool can continue cutting under appropriate cutting conditions while avoiding resonance, and can cut the workpiece while maintaining the quality of the cutting itself such as dimensional accuracy, shape accuracy, and surface roughness. . In addition, if the damping material of the first invention is enclosed in the vibration part over the entire region without being limited to the periphery of the main shaft, the machine tool comprehensively attenuates the entire vibration over the entire region of the main shaft rotation speed to be used. And cutting accuracy can be improved.

  The machine tool can avoid resonance by increasing / decreasing the amount of sealing when resonance occurs, if the amount of damping material sealed is variable.

  When the machine tool is attached to the vibration generating part as required, the detachable reinforcing frame increases the natural frequency of the attaching part by increasing the rigidity of the vibration generating part. Resonance can be avoided and the amplitude can be further reduced.

  If the machine tool is grounded and supported by any three or more support bolts among four or more support bolts that can be raised and lowered attached to a predetermined place on the bottom, for example, primary, The frequency at which vibration modes from the second order to the Nth order are generated can be changed. Such a change in the frequency generated by each mode can change each natural frequency in each direction, avoid resonance, and further reduce the amplitude by combining with the second invention.

Preliminary experiment illustration Illustration of forced vibration analysis Analysis data explanatory diagram Analysis data explanatory diagram Overall illustration Experimental data explanatory diagram Main part explanatory drawing Main part explanatory drawing Experimental data explanatory diagram Experimental data explanatory diagram Experimental data explanatory diagram Experimental data explanatory diagram

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  A high-molecular polymer aqueous solution damping material 11 is characterized in that vibration is attenuated by coming into contact with the surface of a component at a vibration generation site (see FIG. 1A). (B)). A preliminary experiment method for examining the damping ratio of the damping material will be described. The damping ratio of the damping material 11 is such that the center portion of the steel pipe 22 filled with the damping material 11 and suspended by the wire 21 is given an excitation force by the impact hammer 23 from above, and the output corresponding to the generated vibration is given to the center of the steel pipe 22. The logarithmic decay rate measured by the FFT analyzer 24 received from the acceleration sensor 23 attached to the lower part of the unit is obtained on the basis of the measured logarithmic decay rate. That is, the measured logarithmic attenuation rate is data in which the attenuation ratio of the attenuation member 11 and the attenuation ratio of the steel pipe 22 are combined, and the attenuation ratios of the attenuation member 11 and the steel pipe 22 need to be obtained individually. Here, as a method for obtaining the damping ratio of the damping material 11 and the damping ratio of the steel pipe 22, each assumed value is analyzed by a finite element method using a PC 25 (personal computer), and each value is determined according to the obtained result. It is obtained by measuring the work of correcting and re-analyzing until it converges to the logarithmic decay rate. The damping ratio is a parameter indicating the magnitude of vibration of the secondary transfer function, and the amplitude decreases as it increases. The experimental results show that increasing the weight concentration 0%, 2%, 4%, and 6% of the damping material 11 increases the corresponding damping ratio, and the damping ratio of 6% is about 50 times that of 0% water. (FIG. 1B). Further, the damping material 11 having a concentration of 6% or more was not obtained because the pump used in the experiment could not transfer the damping material 11 and thus the damping ratio was not obtained, but the upper limit of the concentration was not 6%. In addition, the steel pipe 22 used for the experiment has a length of 300 mm, a diameter of 48 mm, and a thickness of 2 mm.

  The forced vibration analysis by the finite element method performed using the damping ratio obtained based on the preliminary experiment will be described (FIG. 2A). Such an analysis is provided in a gap 34 provided on a headstock 31a of the tabletop lathe 31 and a frame 36 supporting the headstock 31a based on the shape and size of the tabletop lathe 31 used in an actual experiment. , The enclosure of the damping material 11 (hereinafter referred to as factor 1), the attachment / detachment of the reinforcing frame 32 to / from the motor base 32a (hereinafter referred to as factor 2), and the change of the grounding position of the support bolts 33, 33. (Hereinafter referred to as factor 3), when each parameter is changed and an excitation force of 1 N is periodically applied to the upper part of the tool-side end surface of the head stock 31a in the Y-axis direction, the X-axis direction and Y corresponding to the frequency The compliance corresponding to the amplitude generated in the axial direction is analyzed. However, the X-axis direction is a depth direction with respect to the paper surface of the headstock 31a, and the Y-axis direction is a direction perpendicular to the paper surface of the headstock 31a. In addition, the position of the support bolts 33, 33,... For grounding was set to ABC in the initial state for the analysis of the factor 1 and the factor 2 (FIG. 2B). Note that FIG. 2B is a view of a desktop lathe from the bottom.

  The first analysis model of factor 1 is to change the apparent density change and the attenuation ratio by enclosing the water 34 or the attenuation material 11 having a concentration of 6% in the air gap 34, so that the compliance corresponding to the frequency is obtained. Analysis is performed (FIG. 3A). The amount of water or the attenuation material 11 having a concentration of 6% is changed to four patterns of none, 10 liters, 16 liters, and 22 liters, respectively. As a result of the analysis, when the damping material 11 was sealed in both the X-axis direction and the Y-axis direction, the resonance frequency decreased and the compliance decreased corresponding to the increase in the amount of the damping material 11. In the case of water, the resonance frequency decreased and compliance increased. In addition, as described in the graph of FIG. 3A, 10, 16, and 22 correspond to the amount of the water or the damping material.

  The analysis model of the following factor 1 is that the amount of water or the attenuation material 11 having a concentration of 6% (hereinafter referred to as the attenuation material 11) is set in the gap 37, and there are four patterns of 5 liters, 10 liters, and 13 liters respectively. It was changed (FIG. 3 (B)). As a result of the analysis, when the damping material 11 was sealed in both the X-axis direction and the Y-axis direction, the resonance frequency increased corresponding to the increase in the amount of the damping material 11, and the compliance was reduced. In the case of water, the resonance frequency increased, the compliance in the X-axis direction increased, and the compliance in the Y-axis direction decreased. 3, 5, 10, and 13 correspond to the amount of the water or the damping material.

  The analysis of factor 2 is performed in order to confirm the effect of increasing the rigidity by reinforcing the motor base 32a because the lower-order vibration mode with greater deformation is concentrated in the vicinity of the motor base 32a in the free vibration analysis performed in advance. (FIG. 2 (A)). The reinforcing frame 32 was determined so as to have a size to be used in an actual experiment, and the plate thickness was changed so that the three patterns of 12 mm, 24 mm, and 36 mm and the reinforcing frame 32 were not attached (FIG. 4A). As a result of the analysis, the resonance frequency increased and the compliance decreased in the X-axis direction regardless of the plate thickness. On the other hand, in the Y-axis direction, the frequency of the resonance frequency on the low frequency side increased. Although compliance has increased, on the other hand, compliance has decreased as the resonance frequency on the high frequency side has increased. This result is considered to be due to the presence of a large resonance source in the vicinity of 50 Hz. In this analysis, the case where a hole was provided in the reinforcing frame 32 was also examined. However, the effect was small, and the description thereof was omitted. 4A, the reinforcing frame 32 is not attached, and 12, 24, and 36 correspond to the plate thickness of the reinforcing frame 32.

  Analysis of factor 3 is based on the position of the support bolts 33, 33,... That support the table lathe 31 by grounding, ABC, ABDD, ABBE, ABDE. , A-B-F-G were changed (FIG. 2B). As a result of the analysis, an effect that the resonance frequency can be changed by about 10 Hz to 20 Hz in both the X-axis direction and the Y-axis direction was recognized (FIG. 4B). In addition, ABC, ABD, ABBE, ABDE, and ABFG shown in the graph of FIG. , 33,...

An experiment conducted to confirm the effect in an actual machine will be described. The experiment uses a tabletop lathe 31 based on the analysis by the finite element method, the tool side end surface 31a1 of the headstock 31a has an X-axis direction as a depth direction with respect to the paper surface of the headstock 31a, and the headstock. The acceleration sensors 23, 23 are attached in the Y-axis direction, which is perpendicular to the paper surface of 31a, and set so that the output from the acceleration sensors 23, 23 can be received by the FFT analyzer 25 and measured for vibration. The amplitude of the no-load operation in the X-axis direction and the Y-axis direction was measured by continuously varying the spindle speed of the motor 27 from 600 min ⁻¹ to 3600 min ⁻¹ with the inverter 28 (FIG. 5A). In addition, the name and code | symbol used for description are the same with the desktop lathe used for the analysis by the said finite element method, and the desktop lathe used for experiment.

The tabletop lathe 31 is detachable, and a box-shaped container 34a having a bottom formed of an iron plate having a gap inside and a bottom at the bottom and an open top is provided on a headstock 31a serving as a vibration generating portion. The amount of the attenuation material 11 having a concentration of 6% to be placed and injected into the container 34a was set to 4 patterns of 10 liters, 16 liters, and 22 liters, and the amplitude was measured. The container 34a has a length of 230 mm, a depth of 320 mm, and a height of 345 mm, and is formed corresponding to the dimensions of the depth direction and the length direction horizontal to the paper surface of the headstock 31a. The bottoms on both sides in the depth direction are provided on the horizontal planes formed on both sides in the depth direction of the headstock 31a. The height of the container 34a is a dimension that can be designed and manufactured according to an actual machine, and is manufactured in a size corresponding to the gap 34 used in the finite element method. The results of the measurements, bench lathe 31 regardless of the amount of damping material 11, resonance and spindle speed 996Min ^-1 and spindle speed 2784Min ^-1 in the X-axis direction was observed, spindle speed in the Y-axis direction 2784Min ^A resonance was observed at ⁻¹ (FIG. 6A). As a result of the experiment, the amplitude becomes smaller corresponding to the increase in the amount of the damping material 11. When comparing the case of no water and the injection amount of 22 liters, the amplitude is 84.68% when the spindle speed in the X axis direction is 996 min ⁻¹ reduction and amplitude reduction of 59.55% in the case of spindle speed 2784Min ^-1 is observed, likewise, amplitude reduction of 15.36% in the case of the Y-axis direction of the spindle rotation speed 2784Min ^-1 is observed It was. In addition, as described in the graph of FIG. 6 (A), 10, 16, and 22 correspond to the amount of the damping material. However, the tabletop lathe 31 reflecting the present invention originally includes the gap 34 formed so as to surround the headstock 31a of the vibration generating portion and the damping material 11 enclosed in the gap 34 instead of the container 34a. Thus, the damping material 11 further dampens vibrations more effectively by directly contacting the component surface 31a2 of the head stock 31a when resonance occurs (FIG. 5B). However, the vibration generating part here refers to a part that constitutes the head stock 31a, for example, a part that receives an external forcing force directly via a bearing, and the air gap here is an example of vibration generation. A space in which the damping material 11 for sealing the damping material 11 formed by providing a hole in a part of the part and closing the part with a cover or enclosing the surroundings of the part with a cover does not leak. . Further, the vibration generating portion is shown by taking the head stock 31a as an example, and for example, a feed driving device and a tool fixing device (not shown) are also targeted.

  An example of automation for enclosing the damping material 11 is to transfer the damping material 11 between the machine tool 41, the damping material 11, the tank 42 that accommodates the damping material 11 outside, and the machine tool 41 and the tank 42. What is necessary is just to provide the pump 43 to perform, the valves 44a and 44a, and the valves 44b and 44b. The damping material 11 can be transferred from the tank 42 to the machine tool 41 by opening the valves 44a and 44a and closing the valves 44b and 44b together with the operation of the pump 43. The damping material 11 can be transferred from the machine tool 41 to the tank 42. Conversely, the valves 44a and 44a may be closed and the valves 44b and 44b may be opened (FIG. 5B). In order to make the amount of the damping material 11 variable, the flow rate of the damping material 11 is measured with a sensor (not shown), or the weight of the machine tool 41 is measured with a scale to control the valves 44, 44,. All you need is enough. Note that FIG. 5B shows a table lathe 31 as an example of a machine tool (41), and the arrangement of devices is just an example.

The table lathe 31 is provided with a detachable reinforcing frame 32 around a motor base 32a corresponding to a vibration generating portion, and in particular, in the X-axis direction at a spindle rotation speed of 996 min ⁻¹ in which resonance is recognized in no-load operation. And the Y-axis direction and the amplitude in the Y-axis direction at a spindle rotation speed of 2784 min ⁻¹ were measured (FIGS. 7A and 7B). The reinforcing frame 32 has a length of 265 mm, a depth of 224 mm, and a height of 241 mm. The thickness of the reinforcing frame 32 is changed to 12 mm and 36 mm, and the vertical side surface around the motor base 32a is surrounded from three sides and the lower surface, It is formed so as to be supported by support bolts 32b and 32b, and is structured to be fastened to the motor base 32a with bolts. As a result of the experiment, it is recognized that by attaching the reinforcing frame 32, the amplitude is reduced over the entire range of the main shaft rotation speed and the resonance frequency is increased. In comparison with the case, a decrease in amplitude of 63.47% is observed in the X-axis direction when the spindle speed is 996 min ⁻¹ , and an amplitude decrease of 82.63% is observed when the spindle speed is 2784 min ^−1. In comparison with the case of no reinforcement and the case where the 12 mm reinforcement frame 32 was attached, a decrease in amplitude of 84.27% was observed in the Y axis direction when the spindle rotation speed was 2784 min ⁻¹ . In the experiment, it was also recognized that the effective plate thickness varied depending on the direction of vibration (FIG. 6B). 6B corresponds to the plate thickness of the reinforcing frame 32 without the reinforcing frame 32. In FIG.

  An example of automation for making the reinforcing frame 32 freely attachable / detachable includes a machine tool 41, a reinforcing frame 32, and a hydraulic cylinder 32c for attaching / detaching the reinforcing frame 32 (FIGS. 7C and 7D). By shortening 32c, the end face of the reinforcing frame 32 can be pressed against the machine tool 41 to increase the rigidity. The hydraulic cylinder 32c can be extended and pressed against the end face of the reinforcing frame 32 instead of being shortened, and can be replaced with a pneumatic cylinder or an electric motor. Also, this is not the case if similar movements are possible.

The table lathe 31 supports any three or more of the four or more support bolts 33, 33,... That can be moved up and down attached to the lower locations A, B, C, D, E, F, and G. Spindle speed that can be supported by bolts 33, 33,..., And is grounded by any three or more support bolts 33, 33,. The amplitudes in the X-axis direction and the Y-axis direction at 996 min ⁻¹ and in the Y-axis direction at a spindle rotation speed of 2784 min ⁻¹ were measured (FIG. 8A). The support bolts 33, 33,... Have a basic combination of ABC, and D and E that are symmetrical in the depth direction of C, and F and G that bring D and E closer to the motor base 32a. And prepared for the experiment. The positions of the support bolts 33, 33,... Were changed to five patterns of A-B-C, A-B-D, A-B-E, A-B-D-E, and A-B-F-G. The experimental results show that the resonance frequency fluctuates at the position of the supporting bolt, and in particular, the combination of ABC with the largest amplitude and ABFG with the smallest amplitude. comparing the combination of amplitude reduction of 61.52% in the case of X-axis direction in the spindle speed 996min of 89.65% in the case of ^-1 amplitude reduction and spindle speed 2784Min ^-1 was observed, In the same combination, an amplitude decrease of 88.27% was observed in the Y-axis direction when the spindle rotation speed was 2784 min ⁻¹ (FIG. 9). A-B-C, A-B-D, A-B-E, A-B-D-E, and A-B-F-G described in the graph of FIG. It corresponds to the position of….

  An example of automation for grounding and supporting with arbitrary support bolts 33, 33,... Is a support with male screws corresponding to the female screws 41a, 41a,... Provided in the lower part of the machine tool 41 and the female screws 41a, 41a,. , And electric motors 51, 51, which are connected to the support bolts 33a, 33a,... And are not rotatable relative to the machine tool 41 and are movable in the vertical direction. The support bolts 33, 33,... That rotate with the rotation of 51,... Are grounded via plates 52, 52,. Can be supported on the floor. At this time, if each electric motor 51 is a servo motor capable of strictly controlling the rotation speed, the levelness can be maintained even if it is supported by any three or more support bolts 33, 33,. Therefore, even if the positions of the support bolts 33, 33,... Are changed, the level of the machine tool 41 can be maintained by a predetermined rotation (FIG. 8B). For example, if the machine tool 41 is provided with lifters 53, 53, etc. outside and changes the positions of the support bolts 33, 33,..., Each of the support bolts 33 can be easily rotated. it can.

The table lathe 31 changes the amount of the damping material 11 having a concentration of 6% injected into the container 34a placed on the head stock 31a corresponding to the factor 1 into four patterns of 10 liters, 16 liters, and 22 liters. The reinforcing frames 32 around the motor base 32a corresponding to the factor 2 are respectively attached and detached, and the positions of the support bolts 33, 33,... Corresponding to the factor 3 are set to ABC, AB, respectively. -D, a-B-E, a-B-D-E, varied in 5 pattern of a-B-F-G, 10 places 3600 min ^-1 the spindle speed from 600 min ^-1 under no load FIG. 10A shows the results of factor 1, factor 2 and factor 3 adjusted so that the amplitudes in the X-axis direction and the Y-axis direction become the smallest at a predetermined main shaft rotational speed, and FIG. 10A shows the corresponding amplitude results. 10 (B). This result shows that the combination of factor 1, factor 2 and factor 3 makes it possible to reduce the amplitude evenly over the entire range of the main shaft rotation speed, and the amplitude is suppressed to 1/10 or less in a large resonance. It shows that. In addition, after the adjustment described in the graph of FIG. 10 (B), the result adjusted by combining the factor 1, the factor 2 and the factor 3 is shown, and before the adjustment, the result of nothing is shown. In addition, "-" of the factor 1 of FIG. 10 (A) means that the damping material is not enclosed, and "-" of the factor 2 means that there is no reinforcement.

A table lathe 31 adjusted to factor 1, factor 2 and factor 3 having the smallest amplitude with respect to the main shaft rotation speed of 2784 min ⁻¹ having the largest resonance (hereinafter referred to as an adjusted table lathe 31), a bench lathe 31 not be subjected (hereinafter unadjusted desktop called lathe 31) figure result of comparison by continuously varying the spindle speed from 600 min ^-1 to 3600 min ^-1 without load 11 (a) Shown in Resonance is adjusted for the bench lathe 31 before the adjustment occurs 2784Min ^-1, by bench lathe 31 after the adjustment occurs in 3072 times ^{min -1,} the factor 1 and factor 2 and factor 3 By doing so, it is recognized that the resonance frequency has moved. Further, FIG. 11B shows a cutting condition in which the workpiece is actually cut at the spindle rotational speed of 2784 min ⁻¹ between the adjusted table lathe 31 and the adjusted table lathe 31 before adjustment. The vibration of the tabletop lathe 31 before adjustment has a large amplitude and the individual amplitude itself varies greatly, whereas the vibration of the tabletop lathe 31 after adjustment has an amplitude in the Y-axis direction corresponding to the cutting direction of the tool. It can be seen that it is small and the fluctuations of the individual amplitudes themselves are small (FIG. 12A). As a result, the surface roughness of the workpiece by the tabletop lathe 31 before adjustment is Ra 1.75 μm, while the surface roughness of the workpiece by the tabletop lathe 31 after adjustment is turned despite the turning of the surface roughness of the workpiece. .35 μm is considered to be due to the fact that the amplitude and the fluctuation of the amplitude itself were small (FIG. 12B). “Before adjustment” described in the graphs of FIG. 10B, FIG. 11A, FIG. 12A and FIG. 12B indicates data of the table lathe 31 before adjustment, and “after adjustment”. Shows the data of the tabletop lathe 31 after adjustment.

  The present invention relates to a damping material 11 for reducing resonance of a machine tool and a machine tool using the same, and has industrial applicability.

DESCRIPTION OF SYMBOLS 11 ... Damping material 31a2 ... Component surface 32 ... Reinforcement frame 33 ... Support bolt 34 ... Gap 37 ... Gap 41 ... Machine tool

Claims (4)

It comprises a gap which is provided to surround the component surface of the vibration generating portion, and a damping material of an aqueous solution of the polymer to be sealed in said void, said damping material, said parts being sealed in the gap at resonance occurs A machine tool that is in direct contact with a surface and thereby avoids resonance by increasing the density of the machine tool to lower the natural frequency and attenuate the amplitude. The damping material, the machine tool according to claim 1, characterized in that the filling amount is variable. By mounting the removable reinforcement frame to the vibration generating portion, the machine tool according to claim 1 or claim 2, wherein to avoid resonance. The resonance is avoided by grounding and supporting any three or more of the support bolts that can be raised and lowered attached at a predetermined position on the bottom portion. 1 to a machine tool according to any one of claims 3.

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