JP2001256265A - Method and device for supporting design of gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear design supporting method, with which a gear mechanism is not expanded too much or cost is not increased by previously grasping the dynamic motion of a gear mechanism system. SOLUTION: Concerning the gear design supporting method for analyzing and calculating the dynamic motion of a shaft to be driven corresponding to the motion of a driving shaft by modeling a gear transmission mechanism system installed between the driving shaft and the shaft to be driven, the various element information of basic various elements of a gear and driving condition information are applied (S1), the state of engaging the teeth of the gear is found by using these element information and driving condition information (S3), the contact rigidity value between gears is time sequentially set corresponding to a change in that engaging state (S4), the dynamic motion of the shaft to be driven is calculated by time sequentially solving the equation of motion on the basis of the contact rigidity value (S5-S9) and the calculated operation analyzed result of the driving shaft and the shaft to be driven is outputted (S10).

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an analysis method and an analysis apparatus used for designing a gear mechanism system, and more particularly to a method for realizing a condition close to actual operation by giving basic specifications and driving conditions of a gear. The present invention relates to a gear design support method and a gear design support device capable of estimating a transmission characteristic of a gear mechanism system at a time and checking in advance whether there is any problem with the gear mechanism system.

[0002]

2. Description of the Related Art As a conventional technique for analyzing a meshing state of a gear set including a pair of gears meshing with each other, there is a technique disclosed in, for example, Japanese Patent Application Laid-Open No. 3-100434. In this prior art, after applying paint on the tooth surface of one of the gears of the gear set, the gear set is rotated in a meshed state, and then,
The meshing state of the gear set is analyzed by imaging the peeling state of the paint on the tooth surface of the gear and performing image processing. In addition, a Gleason under load analysis system that analyzes the meshing state under load based on various data on the cutting blade when machining the gears and outputs the tooth contact data has been put into practical use by Gleason Corporation in the United States, Widely used for practical use. Further, as a technology for analyzing a gear mechanism, there is a technology disclosed in Japanese Patent Application Laid-Open No. 6-109593. In this conventional technique, in addition to the data of a gear set including a pinion and a gear, tooth surface data of a pinion and a gear measured by a three-dimensional measuring device after each processing of the gear set are input to a three-dimensional CAD device. Based on the specification data and the tooth surface data of the gear set, a partial model of a pinion in the same coordinate system and a partial model of a gear meshing with the pinion are formed and simulated on a three-dimensional CAD device. To obtain meshing information. In the prior art disclosed in Japanese Patent Application Laid-Open No. 9-016643, the gear shape is visualized, and the meshing state is visually confirmed.

[0003]

[0005] However, the prior art and the Japanese Patent Application Laid-Open No.
The prior art disclosed in Japanese Patent Publication No. 09593 is effective as a method of analyzing the meshing of gears, but has a problem that the behavior when the gears are dynamically operated cannot be completely analyzed. The gear is not a rigid body but an elastic body that is deformed by a load or the like, and also includes a shape error. The dynamic behavior changes variously depending on these factors and operating conditions. If this behavior, that is, the speed that changes every moment, cannot be predicted accurately, the designer must use the safest possible direction (to increase the precision of the gear as much as possible, make the material harder (= heavier), or make the gear larger. Design), and as a result, the size and cost of the gear mechanism have been increased. The object of the present invention is
A gear design support method that solves such problems of the prior art and allows the dynamic behavior of the gear mechanism system to be grasped in advance, so that the gear mechanism does not need to be excessively large and costly to be avoided. To provide.

[0004]

According to the first aspect of the present invention, a gear transmission mechanism system installed between a drive shaft and a driven shaft is modeled to solve the problem of the operation of the drive shaft. In a gear design support method for analyzing and calculating the dynamic behavior of a driven shaft, a specification of basic data of the gear and driving condition information are provided, and the tooth of the gear is determined using the specification information and the driving condition information. The drive calculated by determining the meshing state of the gears, setting the contact stiffness value between the gears in time series in association with the change in the meshing state, and solving the equation of motion in time series based on the contact stiffness value. The method of outputting the operation analysis results of the shaft and the driven shaft was adopted. According to a second aspect of the present invention, in the first aspect of the present invention, the data of the basic specifications of the gear include tooth tip correction shape data, and the tooth tip correction shape data is used to change the gear position. A method was used to correct the contact stiffness value. According to a third aspect of the present invention, in the first aspect of the present invention, the tooth guide corrected shape data is included in the specification information of the basic data of the gear, and the gear tooth gap is formed using the tooth lead corrected shape data. A method was used to correct the contact stiffness value. According to a fourth aspect of the present invention, in the first aspect of the present invention, the data on the basic specifications of the gear includes tooth-to-pitch error data, and the gear-to-gear error is calculated using the pitch-to-pitch error data. A method was used to correct the contact stiffness value. According to a fifth aspect of the present invention, in the first aspect of the present invention, the specification information of the basic data of the gear includes gear assembly error data, and the contact rigidity between the gears is determined by using the assembly error data. The value was corrected. Claim 6
According to the invention described in the first aspect, the specification information of the basic specification of the gear includes the operating environment temperature and the Young's modulus data depending on the temperature, and the operating environment temperature and the Young's modulus data are used. Therefore, a method of correcting the contact stiffness between gears was adopted.

[0005] According to the invention described in claim 7, according to claim 1,
In the described invention, the method of correcting the contact stiffness value between the gears by including the stiffness value of the shaft connected to the gear in the specification information of the basic data of the gear, and adding the stiffness value of the shaft. In the invention according to claim 8, in the invention according to claim 1,
The method of correcting the contact stiffness value between the gears by adding the stiffness value of the bearing that supports the gear in the specification information of the basic specification of the gear and adding the data is used. According to a ninth aspect of the present invention, in the first aspect of the invention, the rigidity value of the frame case that supports the gear is included in the specification information of the basic specification of the gear, and the rigidity value is added to the gear case. Was corrected. According to a tenth aspect of the present invention, there is provided a gear design supporting apparatus for modeling a gear transmission mechanism system installed between a drive shaft and a driven shaft, and analyzing and calculating dynamic behavior of the driven shaft with respect to the operation of the drive shaft. Input means for providing basic gear specification information and driving condition information;
Meshing state calculating means for calculating the meshing state of the gear teeth;
Stiffness setting means for setting a contact stiffness value between gears in a time-series manner in accordance with the meshing state obtained by the meshing state calculating means; and a time-series using a contact stiffness value set by the stiffness setting means. Calculation means for solving the equation of motion
The calculation means includes an output means for outputting the operation analysis result of the driven shaft and the driven shaft obtained by solving the equation of motion.

[0006]

According to the first and the tenth aspects of the present invention, the specification information and the driving condition information of the basic data of the gear are provided, and the specification information and the driving condition are provided. The meshing state of the gear teeth is determined using the information, the contact stiffness value between the gears is set in time series in association with the change in the meshing state, and the motion is performed in time series based on the contact stiffness value. The equations are solved, and the operation analysis results of the drive axis and the driven axis calculated by the equations are output. According to a second aspect of the present invention, in the first aspect of the present invention, tooth tip correction shape data is given as one of the specification information of the basic specifications of the gear, and the tooth tip correction shape data is used by using the tooth tip correction shape data. Is corrected. According to a third aspect of the present invention, in the first aspect of the present invention, tooth lead correction shape data is given as one of the specification information of the basic specifications of the gear, and the tooth lead correction shape data is used by using the tooth lead correction shape data. Is corrected. In the invention according to claim 4, claim 1 is
In the invention described above, inter-pitch error data of the tooth profile is given as one of the specification information of the basic specification of the gear, and the contact stiffness value between the gears is corrected using the inter-pitch error data. According to a fifth aspect of the present invention, in the first aspect of the present invention, gear assembly error data is given as one of the specification information of the basic specifications of the gear, and contact between the gears is performed using the assembly error data. The stiffness value is corrected. According to a sixth aspect of the present invention, in the first aspect of the invention, the operating environment temperature and the temperature-dependent Young's modulus data are given as one of the specification information of the basic specifications of the gear. The contact stiffness value between the gears is corrected using the and the Young's modulus data. According to the seventh aspect of the present invention, in the first aspect of the invention, the rigidity value of the shaft connected to the gear is given as one of the specification information of the basic specifications of the gear, and the rigidity value is added to the gear ratio. Is corrected. Claim 8
In the invention described in the first aspect, the rigidity value of the bearing that supports the gear is given as one of the specification information of the basic specifications of the gear, and the data is added to the contact rigidity value between the gears. Is corrected. According to the ninth aspect of the present invention, in the first aspect of the present invention, the rigidity value of the frame case supporting the gear is given as one of the specification information of the basic specifications of the gear, and the rigidity value is added to the frame case. Is corrected.

[0007]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a functional block diagram of a gear design support device illustrating an embodiment of the present invention. As shown in the figure, the gear design support apparatus of this embodiment has a RAM for temporarily storing programs such as an analysis program and various data, and a CPU that operates in accordance with the program to perform comprehensive control. Unit 1, CRT 2 as a display device for displaying analysis results, etc., and its CR
Keyboard 3 and mouse 4 for inputting data and giving instructions using T2, floppy (registered trademark) disk device (FDD) for inputting and outputting a set of data
5, a printer 6 for outputting analysis results and the like, a magnetic disk device (H) for storing an OS (operating system) for performing basic control of the CPU, an analysis program, and the like.
DD) 7 and the like. The input means described in claim 10 is realized by the keyboard 3 and the mouse 4,
The meshing state calculation means, the rigidity setting means, and the calculation means are realized by the control unit 1, and the output means is realized by the CRT 2 and the printer 6. With such a configuration, in the embodiment of the present invention, the dynamic characteristic of the gear mechanism system is obtained by executing the analysis program, and the information is stored in the cRT2.
The idea is to print it on paper or provide it to designers.
FIG. 2 shows an operation flow of the first embodiment of the present invention.
The operation of this embodiment will be described below with reference to FIG. As shown in FIG. 2, first, basic specification information of a gear to be processed and its driving condition information are inputted by a keyboard 3 or the like (S1). The basic specification information is information such as the number of gear teeth, a module, a pressure angle, a tooth width, a material, a moment of inertia, and a distance between shafts. The drive condition information is, for example, information on an initial angle (direction of a position at which contact with a partner side is started) of the drive gear and drive torque information. After giving these pieces of information, an analysis target operation period of the gear mechanism, an analysis step (analysis time interval), and an analysis allowable error are set as analysis conditions (S2). The gear mechanism transmits power by meshing the teeth on the driving side and the teeth on the driven side, and the meshing of the teeth constantly changes according to the respective rotation angles. The contact force related to the power transmission is obtained as the product of the contact rigidity value and the deflection amount, but the contact rigidity value and the like also change according to the change in the meshing state. Therefore, in the next step, the meshing state at each operation time point (rotational position of the gear) is determined (S
3). Note that the tooth deflection δ is zero when the tooth surfaces are in point contact with each other with no load applied, and when the rotational position of the driving gear is set, the gear position on the driven side is calculated by geometric calculation. (Static analysis: possible with conventional technology). In this state, when the rotation center on the driving side is fixed and a load torque is applied to the driven side, the teeth on the driving side and the driven side are elastically deformed, and the driven side rotates δt (see FIG. 3). The amount of deformation (the amount of deflection δ with respect to load) is related to the contact stiffness value between the gears. The contact stiffness value between the gears differs depending on the position of the meshing teeth, that is, the meshing state. It depends on the basic specifications of the gear, such as the material, face width, and module.

FIG. 4 shows the contact stiffness values at each meshing position in the case of single tooth meshing. In FIG. 4, a, b, and c shown on the horizontal axis are the meshing positions shown in the upper part of FIG. That is, in step S3, it is determined at what position (see FIG. 4) and how each tooth is engaged. The contact rigidity value at each meshing position is
The tooth is modeled as a beam and solved using mathematical formulas, using the finite element method, or actually measured. Next, the contact stiffness value of each gear pair is calculated by adding the contact stiffness values of each tooth pair using the determined meshing state (S4). FIG. 5 shows an example in which the number of meshing teeth is 2 or less (engagement ratio is 2 or less). As can be seen from FIG. 5, the contact stiffness value changes irregularly depending on the number of meshing teeth. At a place where the contact stiffness value is high, two teeth are engaged, and at a place where the contact rigidity value is low, only one tooth is engaged. In each embodiment of the present invention, such a contact stiffness value is represented by Δt (a value specified as an analysis step).
It is stored in a time-series manner in a table format corresponding to each operation time point (rotational position) that is gradually increased. Next, for the first operation time point, the stored contact stiffness value is acquired, and the contact force is calculated as a value obtained by multiplying the added contact stiffness value by the amount of deflection δ (see FIG. 6) (S5). . Further, at the time of this operation (the rotational position on the horizontal axis in FIG. 5,
The contact force at the start of the analysis is substituted into a nonlinear equation of motion (differential equation, see FIG. 6) to solve this equation and determine the balance between the forces on the left and right sides of the two equations (S6). ). That is, it is determined whether or not the error between the drive torque and the corresponding value on the left side and the error between the load torque and the corresponding left side are within the analysis allowable error given in step S2. Numerical solutions to differential equations include the Euler method, the Runge-Kutta method,
Although there are various methods such as the Newmark β method, the description is omitted here.

In the above, when the forces are not balanced (No in S6), the process is repeated from the point that the angle (direction) of the driven gear is slightly changed to obtain the meshing state again (S3 to S6). If the forces are balanced (S
(Yes in 6), the analysis result such as the speed obtained at the operation time is stored (S7), and the operation time is advanced by Δt (the value specified as the analysis step) (S8). Then, it is determined whether or not the stored analysis result has been obtained up to the last operation time point of the analysis target operation period (S9).
(No in 9) Analysis after Δt time is performed in the same manner from step S3. In this way, when the analysis result is obtained until the end of the analysis target operation period (Yes in S9), the analysis result that has been accumulated, for example, the speed at each operation time is output to the CRT 2 or the printer 6 as a graph or a table (S1).
0). The designer looks at the output results and changes gear specifications, drive torque, meshing state, etc. to reduce the speed at meshing positions where the speed etc. is higher than necessary, or meshes too slow. Or increase the speed of the position. That is, according to this embodiment, since dynamic behavior such as speed at each operation time point (rotational position) of the gear mechanism system can be grasped in advance, speed fluctuations and the like can be reduced,
The gear mechanism does not need to be excessively large and costly to achieve the target speed and the like.

FIG. 7 is an operation flowchart showing a second embodiment of the present invention. As shown in the drawing, the operation flow of the first embodiment (see FIG. 2) is obtained by adding a contact rigidity correction step S15 using tooth tip correction shape data given as gear data. It should be noted that the tooth tip correction refers to FIG.
As shown in (a), for example, the tip side of the tooth is shaved by the length L and the correction amount e, whereby contact at the edge on the tip side of the tooth is avoided, and the tooth sharply changes. Has been improved smoothly. That is, in this embodiment, a correction coefficient that changes according to the rotational position, which is a correction coefficient that is multiplied by the contact rigidity value shown in FIG. 5, is obtained, and the contact rigidity value is corrected in step S15. This enables analysis corresponding to the correction of the tooth tip. Note that the correction coefficient is set so that the contact point of the tooth is zero at the base side of the region L, and the contact stiffness value is reduced in the region L in accordance with the amount of deviation from a normal curve (involute curve). . FIG. 8B shows the corrected contact rigidity value. As shown in the figure, according to this embodiment, since the change in the contact stiffness value is smooth, there is an effect that the speed change is smooth, and even in the case of such a tooth tip, an advance analysis is possible. And the same effect as in the first embodiment can be obtained. FIG. 9 is an operation flowchart showing the third embodiment of the present invention. As shown in the figure, the operation flow of the first embodiment (see FIG. 2) is obtained by adding a contact stiffness correction step S35 using tooth trace corrected shape data. Note that the tooth streak correction means changing the shape of the teeth in the width direction as shown in FIG. Accordingly, when the gears are inclined due to an assembly error or the like, it is possible to prevent a tooth contact at an edge in the face width direction. The tooth streak correction includes crowning for rounding the entire tooth width and end relief for chamfering an edge portion of the tooth width (see FIG. 10). In the case where there is no correction, the load is supported by the entire tooth width, but by performing such correction, the area in the width direction is reduced, the teeth are deformed by the magnitude of the load, and the contact area is changed. As a result, when no correction is made, the rigidity value Kb is constant with respect to the deflection amount, but when corrected, the inclination (stiffness value Kb ′) of the graph changes depending on the deflection amount (see FIG. 11). As shown in FIG. 11, when the gears are meshed at the rotation angle θb, the contact stiffness value is Kb without correction, but the stiffness value (inclination of the graph) changes depending on the amount of deflection due to the correction. . This change is treated as a correction coefficient, and by performing correction in step S35, it becomes possible to perform analysis corresponding to the correction of tooth streaks. Thus, according to this embodiment, it is possible to improve the transmission characteristics by increasing the contact force when the amount of deflection increases, and it is possible to perform a preliminary analysis even in the case of such a tooth profile, The same effect as in the first embodiment can be obtained.

FIG. 12 is an operation flow chart showing a fourth embodiment of the present invention. As shown in the figure, a contact rigidity correction step S55 is added to the operation flow of the first embodiment (see FIG. 2) in consideration of the influence of the tooth pitch error. The pitch error of the tooth profile is a variation between the tooth pitches as shown in FIG. 13, and this determines the rotational accuracy. For example, if the tooth is shifted forward by xp compared to the regular pitch, the teeth mesh earlier by xp. Therefore, a correction for shifting the normal contact rigidity by xp in the rotation angle direction is added (see FIG. 14). Since this varies depending on the combination of the number of teeth on the driving side and the number of teeth on the driven side, it is calculated for each meshing tooth and the correction result is stored. Thus, according to this embodiment, such correction enables analysis corresponding to the pitch error of the tooth profile, and even if there is a pitch error, analysis in advance becomes possible. Similar effects can be obtained. FIG. 15 is an operation flowchart showing the fifth embodiment of the present invention. As shown in the figure, the operation flow of the first embodiment (see FIG. 2) is obtained by adding a contact rigidity correction step S75 in consideration of the influence of a gear assembly error. As shown in FIG. 16, when there is no assembly error, the gear is uniform in the direction of the tooth trace (tooth width) (in the case of a spur gear without tooth trace modification). Therefore, the contact area of the tooth surface becomes a line (area) parallel to the rotation axis. On the other hand, if there is an assembly error and the shaft is tilted, the contact area of the tooth surface is not uniform in the direction of the tooth traces but concentrates on a narrower portion between the shafts (one contact), and the contact rigidity of the entire tooth is reduced ( See FIG. 16). Therefore, by correcting the normal contact stiffness value according to the amount of inclination, an analysis corresponding to an assembly error can be performed. Thus, according to this embodiment, even if there is an error in assembling the gears, the analysis can be performed in advance, and the same effect as that of the first embodiment can be obtained.

FIG. 17 is an operation flowchart showing a sixth embodiment of the present invention. In this embodiment, the operating environment temperature and the temperature-dependent Young's modulus data are added to the specification information of the basic specifications of the gear, and as shown in FIG. 17, the operation flow of the first embodiment ( FIG. 2) is added to a contact rigidity value correction step S95 according to the operating environment temperature. As shown in FIG. 18, when a gear is made of a resin that is less susceptible to temperature changes than metal, the Young's modulus (stiffness value) greatly changes at the operating environment temperature. Therefore, the operating environment temperature and the like are also input (S91), and the contact rigidity value of the gear is corrected from the value of this temperature and the Young's modulus depending on the temperature (see FIG. 19) to cope with a material having a large influence on a temperature change. Analysis can be performed. Thus, according to this embodiment, even if the gear is made of a material having a large influence on the temperature change, it is possible to perform a preliminary analysis, and the same effect as in the first embodiment can be obtained. FIG. 20 is an explanatory diagram showing a seventh embodiment of the present invention. In this embodiment, the specification information of the basic data of the gear includes the rigidity of the shaft connected to the gear, and the rigidity is added to correct the contact rigidity between the gears. FIG. 20 shows a model of the contact stiffness of a gear between a motor and a load. If the shaft stiffness is large compared to the gear, the effect is small even if the shaft spring model is removed and analyzed, but if the shaft stiffness is low, the effect is large. Is corrected. For example, the amount of deflection when a load is applied to the position where the gear is mounted on the shaft alone is calculated, the shaft rigidity is calculated from this relationship, and the correction is performed by connecting the spring model of the gear contact rigidity and the spring model of the shaft in series. is there. As a result, according to this embodiment, even in the case where the rigidity of the shaft is low, it is possible to perform an analysis in advance, and the same effect as that of the first embodiment can be obtained. FIG. 21 is an explanatory diagram showing an eighth embodiment of the present invention. In this embodiment,
The rigidity value of the bearing that supports the gear is added to the specification information of the basic specification of the gear, and the rigidity value is added to correct the contact rigidity value between the gears. FIG. 21 shows a model of the contact stiffness of the gear between the motor and the load. If the radial stiffness of the bearing is larger than that of the gear, the influence is small even if the spring model of the bearing is removed and analyzed. In the case where the radial rigidity of the bearing is reduced, the influence is increased. Therefore, in this embodiment, the contact rigidity of the gear is corrected. For example, determine the amount of deflection when a load is applied in the radial direction with a single bearing, calculate the bearing radial rigidity from this relationship,
The correction is performed using a model in which a spring model of the gear contact rigidity and a spring model of the bearing are connected in series. As a result, according to this embodiment, even when the radial rigidity of the bearing is reduced, it is possible to perform an analysis in advance, and the same effect as that of the first embodiment can be obtained.

FIG. 22 is an explanatory diagram showing a ninth embodiment of the present invention. In this embodiment, the rigidity value of the frame case supporting the gears is added to the basic information of the gears, and the contact rigidity value between the gears is corrected by adding the rigidity value. FIG. 22 models the contact stiffness of a gear between a motor and a load. If the rigidity of the frame case is larger than that of the gears, the effect is small even if the frame case spring model is removed and analyzed, but if the rigidity of the frame case is low, this effect increases, It corrects the contact stiffness. For example,
A load is applied in the direction in which the gear contact force acts on the frame case alone, the amount of deflection at that time is calculated, the rigidity in the frame case is calculated from this relationship, and the spring model of the gear contact rigidity and the spring model of the frame case are connected in series. By doing so, it is corrected. Thus, according to this embodiment, even when the rigidity of the frame case becomes low, it is possible to perform an analysis in advance, and the same effect as that of the first embodiment can be obtained.

[0014]

As described above, according to the present invention, the following effects can be obtained. Claim 1 and Claim 10
In the described invention, the specification information and the driving condition information of the basic data of the gear are given, the meshing state of the gear teeth is obtained using the specification information and the driving condition information, and the change of the meshing state is determined. The contact stiffness value between gears is set in time series in correspondence with the equation, and the equation of motion is solved in time series based on the contact stiffness value, and the motion analysis results of the drive shaft and the driven shaft calculated thereby Is output, the dynamic behavior of the gear mechanism system can be grasped in advance, and therefore, a design that reflects the dynamic behavior becomes possible, and the gear mechanism does not need to be excessively large and costly. According to a second aspect of the present invention, in the first aspect, tooth tip correction shape data is given as one of the specification information of the basic specifications of the gear, and the tooth tip correction shape data is used. Since the contact stiffness value between gears is corrected, the change in the contact stiffness value is smoothed, which has the effect of smoothing the speed change, and it is possible to analyze in advance even in the case of such a tooth tip Thus, the same effect as that of the first aspect can be obtained. According to a third aspect of the present invention, in the first aspect of the invention, tooth lead correction shape data is provided as one of the specification information of the basic specifications of the gear, and the tooth lead correction shape data is used. Since the contact stiffness value between gears is corrected, it is possible to improve the transmission characteristics by increasing the contact force when the amount of deflection increases, and it is possible to perform advance analysis even in the case of such a tooth profile Thus, the same effect as the first aspect can be obtained. Also,
According to a fourth aspect of the present invention, in the first aspect of the present invention, the pitch error data of the tooth profile is given as one of the specification information of the basic data of the gear, and the gear error is determined using the pitch error data. 2. Since the contact stiffness value is corrected, a prior analysis is possible even if there is an error between pitches.
The same effect as the described invention can be obtained.

[0015] According to the fifth aspect of the present invention, in the first aspect,
In the described invention, assembling error data of the gear is given as one of the specification information of the basic data of the gear, and the contact rigidity value between the gears is corrected using the assembling error data. Even if there is an error, the analysis can be performed in advance, and the same effect as that of the first aspect can be obtained. According to a sixth aspect of the present invention, in the first aspect of the invention, the operating environment temperature and the temperature-dependent Young's modulus data are given as one of the specification information of the basic specification of the gear. Since the contact stiffness value between the gears is corrected using the environmental temperature and the Young's modulus data, even if the gears are made of a material having a large influence on the temperature change, it is possible to perform a preliminary analysis. Similar effects can be obtained. Further, according to the invention described in claim 7, according to claim 1,
In the described invention, a stiffness value of a shaft connected to the gear is given as one of the specification information of the basic specification of the gear, and the contact stiffness value between the gears is corrected by adding the stiffness value.
Prior analysis is possible even when the rigidity of the shaft is low, and the same effect as the first aspect can be obtained. According to an eighth aspect of the present invention, in the first aspect of the present invention, the rigidity value of the bearing supporting the gear is given as one of the specification information of the basic specification of the gear, and the data is added thereto. Since the contact stiffness value between the bearings is corrected, even if the radial stiffness of the bearing is reduced, it is possible to perform an analysis in advance, and the same effect as the first aspect of the invention can be obtained. According to the ninth aspect of the present invention, in the first aspect of the invention, the rigidity value of the frame case supporting the gear is given as one of the specification information of the basic specification of the gear, and the rigidity value is added. Since the contact stiffness value between the gears is corrected, even if the rigidity of the frame case is low, it is possible to perform an analysis in advance, and the same effect as the first aspect can be obtained.

[Brief description of the drawings]

FIG. 1 is a configuration block diagram illustrating a gear design support device according to each embodiment of the present invention.

FIG. 2 is an operation flowchart of a gear design support method according to the first embodiment of the present invention.

FIG. 3 is an explanatory diagram of a gear design support method according to the first embodiment of the present invention.

FIG. 4 is another explanatory diagram of the gear design supporting method according to the first embodiment of the present invention.

FIG. 5 is another explanatory diagram of the gear design supporting method according to the first embodiment of the present invention.

FIG. 6 is another explanatory diagram of the gear design supporting method according to the first embodiment of the present invention.

FIG. 7 is an operation flowchart of a gear design support method according to a second embodiment of the present invention.

FIG. 8 is an explanatory diagram of a gear design support method according to a second embodiment of the present invention.

FIG. 9 is an operation flowchart of a gear design support method according to a third embodiment of the present invention.

FIG. 10 is an explanatory diagram of a gear design support method according to a third embodiment of the present invention.

FIG. 11 is another explanatory view of the gear design supporting method according to the third embodiment of the present invention.

FIG. 12 is an operation flowchart of a gear design support method according to a fourth embodiment of the present invention.

FIG. 13 is an explanatory diagram of a gear design support method according to a fourth embodiment of the present invention.

FIG. 14 is another explanatory diagram of the gear design supporting method according to the fourth embodiment of the present invention.

FIG. 15 is an operation flowchart of a gear design support method according to a fifth embodiment of the present invention.

FIG. 16 is an explanatory diagram of a gear design support method according to a fifth embodiment of the present invention.

FIG. 17 is an operation flowchart of a gear design support method according to a sixth embodiment of the present invention.

FIG. 18 is an explanatory diagram of a gear design support method according to a sixth embodiment of the present invention.

FIG. 19 is another explanatory diagram of the gear design supporting method showing the sixth embodiment of the present invention.

FIG. 20 is an explanatory diagram of a gear design support method according to a seventh embodiment of the present invention.

FIG. 21 is an explanatory diagram of a gear design support method according to an eighth embodiment of the present invention.

FIG. 22 is an explanatory diagram of a gear design support method according to a ninth embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Control part 2 CRT 3 Keyboard 4 Mouse 5 Floppy disk device 6 Printer 7 Magnetic disk device

Claims (10)

[Claims] 1. A gear design supporting method for modeling a gear transmission mechanism system installed between a drive shaft and a driven shaft, and analyzing and calculating dynamic behavior of the driven shaft with respect to the operation of the drive shaft. Given the specification information and driving condition information of the basic specifications possessed, the meshing state of the gear teeth is determined using the specification information and the driving condition information, and the contact stiffness value between the gears is associated with the change in the meshing state. A gear design support method characterized in that a time series is set in a time series, and a motion analysis result of a drive shaft and a driven shaft calculated by solving a motion equation in a time series based on the contact stiffness value is output. 2. The gear design support method according to claim 1, wherein the specification information of the basic data of the gear includes tooth tip correction shape data, and the contact rigidity between the gears is determined using the tooth tip correction shape data. A gear design support method comprising correcting a value. 3. The gear design support method according to claim 1, wherein the specification information of the basic specifications of the gear includes tooth lead correction shape data, and the contact stiffness between the gears is used by using the tooth lead correction shape data. A gear design support method comprising correcting a value. 4. The gear design supporting method according to claim 1, wherein the data on the basic specifications of the gear include error data of the pitch of the tooth profile, and the contact stiffness between the gears is determined by using the error data of the pitch. A gear design support method comprising correcting a value. 5. The gear design support method according to claim 1, wherein the specification information of the basic specification of the gear includes gear assembly error data, and the contact stiffness value between the gears is determined using the assembly error data. A gear design support method characterized by correcting. 6. The gear design support method according to claim 1, wherein the specification information of the basic specification of the gear includes operating environment temperature and Young's modulus data depending on the temperature, and the operating environment temperature and Young's modulus are included. A gear design support method, wherein a contact stiffness value between gears is corrected using data. 7. The gear design supporting method according to claim 1, wherein the specification information of the basic specification of the gear includes a stiffness value of a shaft connected to the gear, and the stiffness value is added to the contact stiffness between the gears. A gear design support method comprising correcting a value. 8. The gear design supporting method according to claim 1, wherein the specification information of the basic specification of the gear includes a stiffness value of a bearing supporting the gear, and the data is added to the contact stiffness value between the gears. A gear design support method characterized by correcting the following. 9. The gear design supporting method according to claim 1, wherein the specification information of the basic specification of the gear includes a rigidity value of the frame case supporting the gear, and the rigidity value is added to the contact between the gears. A gear design support method characterized by correcting a rigidity value. 10. A gear design support apparatus for modeling a gear transmission mechanism system installed between a drive shaft and a driven shaft and analyzing and calculating dynamic behavior of the driven shaft with respect to the operation of the drive shaft. Input means for providing the specification information of the specifications and the driving condition information; meshing state calculating means for calculating the meshing state of the gear teeth; Stiffness setting means for setting a contact stiffness value in time series, calculation means for solving a motion equation in time series using the contact stiffness values set by the stiffness setting means, and the calculation means solving the motion equation A gear design support device comprising: a driving shaft obtained by the above operation; and an output unit for outputting a result of operation analysis of the driven shaft.