JP2014240685A - Gear design support method, program and device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear design support method capable of analyzing dynamic behavior with sufficient analysis accuracy even to shaft vibration dynamically changing.SOLUTION: In a deflection amount calculation step of obtaining a deflection amount of a gear on a gear action line corresponding to a rotation direction in between meshing gears, the deflection amount is obtained by summing the difference of products of a gear rotation angle and a basic circle radius between the meshing gears, a changed part of a contact distance, a product of a changed part of a drive side contact angle and a drive side basic circle radius, a product of a changed part of a driven side contact angle and a driven side basic circle radius, and a changed part calculated from a deflection angle of a bearing part and a tooth width meshing position.

Description

  The present invention relates to a gear design support method, program, and apparatus for modeling a gear transmission mechanism system provided on a drive shaft and a driven shaft and analyzing the dynamic behavior of the driven shaft with respect to the operation of the drive shaft.

  2. Description of the Related Art Conventionally, as a gear design support, a method for predicting a life by providing an encoder on a driving side and a driven side of a gear pair and measuring it is known. However, with this method, it is impossible to predict that there is no actual object, so it is not possible to provide gear design support.

For this reason, Patent Document 1 is known as a gear design support method for performing prediction in a virtual space.
With reference to Patent Document 1, by setting the gear shape error, driving conditions, bearing rigidity of the gear support structure, and calculating the amount of change in the deflection due to translational motion, the rotational transmission characteristics and gear vibration force can be calculated. A configuration for prediction is described.

  However, Patent Document 1 described above sequentially analyzes the tooth surface position change amount according to the value of the inter-axis fluctuation amount so that the influence of the translational motion can be taken into account. However, the inclination direction (the declination direction: θx). , Θy), the analysis accuracy may be reduced.

  As products become smaller and lighter, bearings tend to increase in bearing clearance and clearance due to wear due to the application of inexpensive plastic sliding bearings. Also, the bearing support structure has a tendency to decrease the bearing rigidity due to the conversion to a sheet metal with a thin plate thickness. In such a case, translational vibration and deviated vibration between axes, which has not been a problem in the past, may affect the rotation unevenness, and a design support tool that can predict this at the design stage has been strongly desired.

  The present invention has been made in view of such a situation, and an object thereof is to provide a gear design support method capable of analyzing dynamic behavior with sufficient analysis accuracy even with respect to dynamically changing shaft vibration. To do.

  In order to achieve this object, the gear design support method according to the present invention models the gear transmission mechanism system provided on the drive shaft and the driven shaft, and shows the dynamic behavior of the driven shaft with respect to the operation of the drive shaft. In a gear design support method executed by a computer to be analyzed, a basic input step for receiving input of specification information and driving condition information of a gear to be analyzed, and a gear bearing for receiving input of information relating to a bearing that rotatably supports the gear Deflection amount calculation step for obtaining the deflection amount of the gear on the gear action line corresponding to the rotation direction between the meshing gears based on the input in the information input step, the basic input step and the gear bearing information input step, and the deflection amount And calculating the meshing force from the product of the tooth pair rigidity and generating a motion equation for the tooth pair contacting on the gear action line, and the motion equation A time series calculation step that solves in series, and in the deflection amount calculation step, the deflection amount is determined by calculating the difference between the product of the gear rotation angle and the basic circle radius between the meshing gears, the change in the contact distance, and the contact on the drive side. Product of angle change and driving side basic circle radius, product of driven side contact angle change and driven side basic circle radius, and change calculated from bearing part deflection angle and tooth width meshing position It is characterized by calculating | requiring as a sum total of.

  As described above, according to the present invention, it is possible to provide a gear design support method capable of analyzing dynamic behavior with sufficient analysis accuracy even for dynamically changing shaft vibrations.

It is a flowchart which shows the calculation procedure by 1st Embodiment. It is a figure explaining the relationship of each parameter in the derivation formula of deflection amount (psi). It is a figure which shows the basic | foundation circle | round | yen and gear action line | wire between meshing gears. It is a figure explaining the relationship of each parameter relevant to the deflection angles (theta) x and (theta) y in the derivation | leading-out formula of the deflection amount (psi). It is a figure explaining the relationship of each parameter in the equation of motion of a gearwheel. It is a figure which shows an example of the meshing force for every meshing tooth pair. It is a figure which shows an example of the meshing force Ft. It is a figure which shows the example of an analysis result in a rotation angle error. It is a figure which shows an example of bearing deflection angle (theta) x. It is a figure which shows the example of an analysis result in a prior art. It is a figure which shows the example of an analysis result by 1st Embodiment. It is a flowchart which shows the operation | movement used as the content of the time series calculation process in 1st Embodiment. It is a flowchart which shows the operation | movement used as the content of the time series calculation process in 3rd Embodiment. It is a figure which shows the support structural example in the bearing part of a gearwheel. It is a flowchart which shows the operation | movement used as the content of the time series calculation process in 6th Embodiment. It is a figure which shows the power transmission mechanism 50 which rotates a photoreceptor drum. It is a figure which shows the power transmission mechanism 60 which rotates a transfer belt. It is a block diagram which shows the structural example around the gear design assistance apparatus 1 by 9th Embodiment. It is a block diagram which shows the structural example surrounding the gear design assistance apparatus 1 by 10th Embodiment.

  Next, an embodiment to which the gear design support method according to the present invention is applied will be described in detail with reference to the drawings.

Each embodiment relates to a gear design support method, a recording medium recording a gear design support program, and a gear design support device. Specifically, the gear mechanism in a state close to actual operation is provided by providing basic specifications of the gear, drive information, error information (gear shape error), and information such as a rotating bearing and a gear support structure for rotating and supporting the gear. It is possible to estimate the transmission characteristics of the system and the gear excitation force that is the vibration source at the time of meshing.
Each embodiment relates to a gear design support device, a gear design support method, and a recording medium that can confirm whether there is a problem related to the gear mechanism system in advance.

  For this reason, each embodiment can be applied to an image forming apparatus such as a copying machine or a printer, and can be applied to design processes in a wide range of fields such as information equipment, home appliances, and robots that are precision machine products using a gear mechanism system. Can do.

[First Embodiment]
Next, a first embodiment will be described.
FIG. 1 shows a calculation flowchart of the analysis program according to the first embodiment. As an analysis procedure, first, in the basic input process, basic specification information of the gear to be analyzed and its driving condition information are input (step S1). The basic specification information includes the number of gear teeth, the tooth size module, tooth pressure angle, tooth helix angle, gear tooth width, gear material, gear moment of inertia, and the distance between gears. Etc. The driving condition information includes, for example, initial angles of the driving gear and the driven gear (which tooth starts to engage with which tooth), a target speed or driving torque applied to the driving shaft, and a load torque applied to the driven shaft.

  Next, as information on the bearing for rotating and supporting the gear, the clearance of the rotating shaft, the bearing translation spring stiffness, the bearing deflection spring stiffness, the bearing translation damping coefficient, and the bearing deflection damping coefficient are given in the gear bearing information input step (step S2). ). For example, if there is a gap in the bearing, the gear moves in translation within the gap, so the gap amount is set. Alternatively, when the bearing spring rigidity is small, translational motion and declination motion are performed according to the load applied to the gear. The bearing spring stiffness and damping coefficient are set. Here, the declination spring rigidity and declination attenuation coefficient to be set are values of two-direction components (around the X axis and around the Y axis), respectively.

  After these data are given, the analysis target operation time of the gear drive system and the analysis step (analysis time interval) are set as analysis conditions (step S3). The gear drive system transmits power by meshing the driving-side teeth and the driven-side teeth, and the meshing of these teeth constantly changes according to the respective rotation angles. The meshing force Ft, which is a contact force between teeth involved in power transmission, is obtained as a product of a contact stiffness (tooth-to-rigidity) value Kt and a deflection amount ψ.

Therefore, in this embodiment, the deflection amount ψ is obtained by the following equation (step S4).
ψ = ψa + ψb + ψc + ψd + ψe

Each of ψa to ψe will be described with reference to FIGS.
ψa is the difference between the product of the gear rotation angle (θz1, θz2) and the basic circle radius (rb1, rb2), and is obtained by the following equation.
ψa = rb1 · θz1−rb2 · θz2

ψb is the change ΔLg in the contact distance, and is obtained by the following equation.
ψb = ΔLg = Lg′−Lg
However, Lg ′ is an initial contact distance and is obtained by the following formula.
Lg ′ = SQRT {(x2′−x1 ′) ² + (y2′−y1 ′) ² − (rb1 + rb2) ² }
However, (x1 ′, y1 ′) is the initial driving gear basic circle coordinates, and (x2 ′, y2 ′) is the initial driven gear basic circular coordinates.

ψc is a product of the change Δφ in the drive side contact angle and the drive side basic circle radius rb1, and is obtained by the following equation.
ψc = Δφ · rb1 = (φ′−φ) · rb1
However, φ ′ is an initial contact angle, that is, an angle from the x-axis to the contact position, and is obtained by the following equation.
φ ′ = α′−θj ′
Where α ′ is the initial pressure angle and θj ′ is the initial inter-axis angle.

ψd is the product of the change Δφ of the driven side contact angle and the driven side basic circle radius rb2, and is obtained by the following equation.
ψd = Δφ · rb2 = (φ′−φ) · rb2

ψe is a change calculated from the deflection angles θx and θy of the bearing portion and the tooth width meshing position Lb, and is obtained by the following equation.
ψe = − (Lb · θx · cos α) + (Lb · θy · sin α)
However, the tooth width b is set to −b / 2 ≦ Lb ≦ + b / 2. Lb indicates the meshing position in the tooth width direction, and is a value with the center of the tooth width set to zero.

  As described above, in this embodiment, the deflection amount ψ is obtained from the sum of the five components ψa, ψb, ψc, ψd, and ψe.

  As a comparison between the present embodiment and the prior art, most of the conventional analysis of gears so far requires only the component of ψa for transmission of rotational motion, and some prior art However, only the translational motion of the bearing was considered.

FIG. 3 schematically shows a basic circle and a gear action line between gears meshing with an involute tooth profile.
Involute tooth profiles occupy most of the tooth surface shapes of the gears, and the meshing of the tooth surfaces can be regarded as the movement of a marking belt provided with a tangent line on the basic circle of each gear as shown in FIG. This tangent is the gear action line. Depending on the direction of rotation, the belt application changes. The belt mechanism transmits power by pulling, while the gear transmits power by pushing. In the case of a belt, the magnitude of the power (transmission force) changes according to the difference between the winding and unwinding of both pulleys. This difference amount becomes the belt elongation, and the belt tension is obtained by applying the spring rigidity of the belt to the belt elongation. Considering the case where the pulley moves in translation, the distance between the contacts changes with the translation of the pulley, and the belt also expands and contracts. In addition, the position of the contact point between the pulley and the belt changes, and the belt expands and contracts due to this. By replacing these components with gears, it is possible to formulate each component.

  Here, when the gear moves in translation, the point of contact on the tooth surface changes. In the case of a belt drive system, this is a form in which the belt is excessively wound or unwound on the pulley, resulting in a change in tension. In the present embodiment, the same function can be considered for the gear drive system, and this mechanism is reflected in the mathematical expression.

  Further, in the prior art based on the consideration up to the translational motion of the bearing, there is no problem if the gear shaft deflection angles θx and θy are small. Therefore, in the present embodiment, a change calculated from the deflection angles θx and θy of the bearing portion and the tooth width meshing position Lb [ψe = − (Lb · θx · cosα) + (Lb · θy · sinα) as ψe. ], The meshing force is calculated from the deflection amount ψ of the five components.

  As shown in FIG. 4, when the shaft is deviated at the meshing point in the tooth width direction (center of the meshing tooth width), the contact point is offset. By adding this change in numerical form, the meshing force Ft corresponding to the declination angles θx and θy can be obtained sequentially.

  Next, in the equation of motion derivation, the equation of motion, which is a differential equation, is calculated for each gear using the deflection amount ψ and the meshing force Ft thus obtained (step S5). The equation of motion of the gear is expressed by the following equation when an arbitrary gear having an axial rotation direction (θ) and a translational direction (x, y) is determined with reference to the explanatory diagram of FIG.

  Next, in the time series calculation step, this equation of motion (differential equation) is simultaneously solved and solved in time series (step S6). Here, the balance of this force is obtained every minute time (each analysis step), and the calculation is advanced. As a numerical solution method, a general Euler method, a Runge-Kutta method, a Newmark β method, or the like that solves a differential equation can be used, and the description is omitted here.

  When the predetermined time is analyzed in the steady state, the meshing force for each meshing tooth is obtained as shown in FIG. An example of the meshing force Ft as a sum of these is shown in FIG. The meshing force Ft becomes a force (torque) for driving the gear, and the reaction force is applied to the bearing, and becomes a gear vibration force that applies vibration to the entire apparatus. Rotational unevenness is caused by the fluctuation component of the gear driving force meshing cycle.

  After that, when the analysis time ends (step S7; Yes), the analysis results accumulated so far in time stepwise are output as graphs and tables to a display display or printer, or stored as data in a recording medium. (Step S8). The analysis results are, for example, the rotational characteristics shown in FIG. 8 such as the angular transmission error with respect to the time of the drive shaft and the driven shaft, the angular velocity transmission error, and the gear vibration force as the reaction force of the meshing force applied to the bearing. is there.

  Next, a comparison between the analysis result of the conventional technique based on the above-described consideration of the translational motion of the bearing and the analysis result based on the present embodiment will be described with reference to FIGS. Here, as shown in FIG. 9, a minute deflection vibration (θx = 0.0017 · sin (2 · π · f · t) [rad], frequency f = 80 Hz) is applied in the bearing deflection angle θx direction, and driving is performed. An analysis example for obtaining rotation unevenness when the entire side gear is vibrated will be described.

  FIG. 10 shows an example of the analysis result of this prior art. In the analysis result of the prior art shown in FIG. 10, the speed unevenness is uniform, and when the speed unevenness component is seen by frequency analysis, the 80 Hz component is not seen, and only the meshing cycle related component is found.

  On the other hand, the example of the analysis result by this embodiment is shown in FIG. In the analysis result according to the present embodiment shown in FIG. 11, the speed unevenness is fluctuating, and the 80 Hz component which is the vibration component of the bearing deflection angle θx can be confirmed by analyzing the frequency and examining the component of the speed unevenness. As described above, when the gear is subjected to deviating vibration or when it is vibrated in the declination direction due to the meshing force, the analysis of this embodiment can be performed to determine its rotational characteristics (speed unevenness, etc.) The vibration force can be predicted.

  As described above, in the first embodiment described above, the influence of the design parameters such as the gear specifications, the rotation support configuration of the gear, and the drive conditions, which are the design parameters that affect the rotation transmission characteristics and the gear vibration force of the gear. The purpose of this is to predict in advance by a short analysis. At that time, the analysis is performed in consideration of the dynamic behavior due to the influence of the resonance phenomenon, the translational movement, the influence of the declination vibration of the shaft, etc. This provides a gear design support method that can easily and accurately support gear design without checking the gear mechanism system for problems, eliminating the need to prototype and evaluate the gear drive system. For the purpose.

Therefore, the first embodiment described above models a gear transmission mechanism system installed between the drive shaft and the driven shaft, and analyzes and calculates the dynamic behavior of the driven shaft with respect to the operation of the drive shaft. The design support method includes the following steps.
(1) Basic input process that receives input of basic specification information of gears to be analyzed and driving condition information of target speed and load torque. (2) Clearance between rotating shaft and bearing for rotation support of gear. Gear bearing information input process for receiving information on bearing stiffness, bearing spring stiffness, bearing damping coefficient (translation direction XYZ, rotation direction θz, declination direction θx, θy) (3) The basic input process and gear bearing information input process Deflection amount calculation process (4) Determining the amount of deflection when the tangent (gear line of action) corresponding to the direction of rotation is obtained by obtaining information on the center circle center coordinates and the base circle radius of the gear and engaging the gear on this tangent line (4) The meshing force is calculated from the product of the tooth-to-tooth stiffness, and the equation of motion is derived for generating the equation of motion for the tooth-pair in which these forces are in contact with the gear action line (5). When solving Column calculating step (6) time series calculation calculated drive shaft of the step and the output step of outputting the operation result of the driven shaft

In the deflection amount calculation step, the deflection amount ψ is obtained as the sum of the five components ψa, ψb, ψc, ψd, and ψe. However,
ψa is the difference between the product of the gear rotation angle and the basic circle radius between the meshing gears ψb is the contact distance change ψc is the product of the drive side contact angle change and the drive side basic circle radius ψd is the driven The product of the change in the side contact angle and the driven side basic circle radius ψe is the change calculated from the deviation angle of the bearing and the tooth width meshing position.

  In this embodiment, gear deflection vibration, which is one of the factors that generate rotation unevenness and gear vibration force, is incorporated into the analysis program, and the amount of change in deflection due to this deflection vibration is calculated strictly, and rotation while meshing. It becomes possible to analyze the dynamic behavior of gears that vibrate and deviate.

As a result, the influence of design parameters such as gear specifications, gear rotation support configuration, and driving conditions, which influence the gear rotation transmission characteristics and gear vibration force, are predicted in advance and in a short time analysis. be able to. At that time, the analysis is performed considering dynamic behavior. This dynamic behavior is due to the influence of the inertial term and the rotational speed, such as the influence of resonance phenomenon, translational movement, and shaft deflection vibration.
As a result, it is possible to easily support the gear design with high accuracy without checking the gear mechanism system for problems and eliminating the work of making and evaluating the gear drive system.

  According to the present embodiment, as described above, the dynamic behavior can be analyzed with sufficient analysis accuracy even for the deflection vibration of the dynamically changing shaft. For this reason, it is possible to provide a gear design support method capable of providing sufficient design support from a design stage without a real object even for a gear transmission mechanism system that has been reduced in size and weight.

[Second Embodiment]
Next, a second embodiment will be described.
In the second embodiment, the deflection correction amount ψf is calculated from gear shape error information such as a gear tooth shape error, a tooth streak error, and a cumulative pitch error, and this value is the deflection amount calculating step of the first embodiment described above. In addition, the amount of deflection ψ is obtained from the sum of the six components.

  When the shape error of the tooth surface becomes larger than the amount of deflection, the degree of influence on the analysis result increases. Therefore, in the second embodiment, an error at the tooth surface position that is engaged is obtained from information on a tooth profile error, a tooth streak error, and a cumulative pitch error as a tooth surface shape error (gear shape error), and this value is bent. The correction amount ψf is added to the equation of the deflection amount ψ in the first embodiment.

For this reason, the deflection amount ψ in the second embodiment is obtained by the following equation.
ψ = ψa + ψb + ψc + ψd + ψe + ψf
However,
ψf = δa + δb + δc
δa is the tooth profile error at the meshing point between the driving gear and the driven gear δb is the tooth trace error at the meshing point between the driving gear and the driven gear δc is the accumulated pitch error at the meshing point between the driving gear and the driven gear

As described above, in the second embodiment, the deflection amount ψ is calculated from the six components including the deflection correction amount ψf based on the gear shape error information such as the gear tooth profile error, the tooth trace error, and the cumulative pitch error. For this reason, the fluctuation component of the meshing force accompanying the tooth surface shape error can be calculated.
As a result, the calculation prediction accuracy can be improved even when the shape accuracy of the target gear is not good.

[Third Embodiment]
Next, a third embodiment will be described.
In the third embodiment, in the time series calculation process, the product of the gear tooth width and the deflection angle of the bearing portion is compared with the magnitude of the gear shape error, and the product of the tooth width and the deflection angle is large. Only the change ψe calculated from the deviation angle and the tooth width meshing position is taken into consideration.

  FIG. 12 shows operations that are the contents of the time-series calculation process in the first embodiment described above. FIG. 13 shows the operations that are the contents of the time series calculation process in the third embodiment.

  In the time series calculation process in the first embodiment, as shown in FIG. 12, first, the initial time setting is set to t = 0 (step S11), and a differential equation in a minute time as one analysis step is solved (step S12). , S13). When the data as the calculation result is stored (step S14), the analysis step is advanced by one (step S15), and the operation for solving the differential equation in minute time as the next analysis step is repeated. In this way, the differential equations are sequentially solved every minute time as each analysis step.

  In the time series calculation process in the third embodiment, as shown in FIG. 13, first, the initial time setting is set to t = 0 (step S21). Then, the product ψe ′ of the deflection angles θx, θy and the tooth width Lb is obtained and compared with the set gear shape error ψf (step S22).

  When ψe ′ is larger than ψf, the differential equation in minute time as one analysis step is solved similarly to the operation of the first embodiment shown in FIG. 12 (step S23), the data is stored, and the next The process proceeds to a minute time as an analysis step (steps S27 and S28).

  When ψe ′ is equal to or less than the value of ψf, the above-described ψe, which is a correction by the declination angles θx and θy, is excluded (step S24), and a differential equation in a minute time as one analysis step is solved (step S25). Then, the data is saved and the process proceeds to a minute time as the next analysis step (steps S27 and S28).

  As described above, in the third embodiment, in the time series calculation step, the product ψe ′ of the gear tooth width Lb and the bearing portion deflection angles θx and θy is compared with the magnitude of the gear shape error ψf. . Only when the product ψe ′ of the tooth width Lb and the deflection angles θx, θy is larger, the change calculated from the bearing portion deflection angles θx, θy and the tooth width meshing position Lb [ψe = − (Lb · θx • cos α) + (Lb · θy · sin α)].

In this way, in the time series calculation process of solving the differential equation in a minute time step, the product of the deviation angle and the tooth width is compared with the set gear shape error value, and the change ψe due to the deviation angle is determined by this magnitude. Determine whether to add. For this reason, the influence of declination can be taken into account only when the tooth width is large or the declination is large, and when the influence of the gear shape error is larger, the influence of declination is excluded and analyzed. be able to.
As a result, only when the influence of the deflection angle is large, the change ψe due to the deviation angle and the tooth width meshing position is taken into consideration, and high-speed calculation can be performed. For this reason, the efficiency of analysis work can be improved.

[Fourth Embodiment]
Next, a fourth embodiment will be described.
In the fourth embodiment, in the time series calculation process, the change ψe calculated from the declination angle and the tooth width meshing position is considered only when the gear bearing portion is a cantilever type.

  FIG. 14 shows an example of a gear support structure. FIG. 14A shows a case where the bearing portion is a cantilever type, and FIG. 14B shows a case where the bearing portion is a cantilever type.

  Compared to the double-supported type in which the bearings are on both sides with respect to the tooth surface position of the gear as shown in FIG. 14 (a), the cantilevered type in which the bearing is only one side as shown in FIG. 14 (b). The deflection angle increases due to the tooth surface load and the bearing deflection spring stiffness. For this reason, only when the supporting structure of the gear is a cantilever type, the amount of change due to declination is taken into consideration.

As described above, in the fourth embodiment, in the time series calculation process, only when the gear bearing portion is a cantilever type, the bearing portions are calculated from the deflection angles θx and θy and the tooth width meshing position Lb. Consider the change [ψe = − (Lb · θx · cos α) + (Lb · θy · sin α)]. That is, the differential equation in minute time as one analysis step is solved similarly to the operation of the first embodiment described above.
In the case of a double-supported bearing with a small declination, the above-described ψe, which is a correction amount based on the declination angles θx and θy, is excluded, and a differential equation in a minute time as one analysis step is solved.

For this reason, it is possible to accurately model the deflection angle that is likely to occur due to the support configuration (bearing system) in the bearing portion of the gear.
As a result, only when the influence of the deflection angle is large, the change ψe due to the deviation angle and the tooth width meshing position is taken into consideration, and high-speed calculation can be performed. For this reason, the efficiency of analysis work can be improved.

[Fifth Embodiment]
Next, a fifth embodiment will be described.
In the fifth embodiment, only the misalignment direction (θx) is considered among the deviation angles ψe of the change ψe due to the deviation angle and the tooth width meshing position described above.

In the first to fourth embodiments described above, the change ψe due to the deflection angle and the tooth width meshing position is obtained by the following equation.
ψe = − (Lb · θx · cos α) + (Lb · θy · sin α)
In the fifth embodiment, ψe is obtained by the following equation.
ψe = − (Lb · θx · cos α)

  When the rotation axis is Z and the inter-gear axis direction is the X-axis, the direction around the X-axis is θx, and the tooth surfaces are in mesh with each other by the deviation angle θx. Comparing the degree of influence when the same declination is applied to θy and θx, this declination θx is 2.7 times larger (= cos α / sin α), so this value is used.

As described above, in the fifth embodiment, only the staggering direction (θx) between the meshing gears is considered among the declination of the gear in the change ψe due to the declination and the tooth width meshing position. For this reason, the calculation formula of the change ψe depending on the deviation angle and the tooth width meshing position can be simplified.
As a result, only the discrepancy direction in which the degree of influence of the deflection angle is large is considered, and high-speed calculation can be performed. For this reason, the efficiency of analysis work can be improved.

[Sixth Embodiment]
Next, a sixth embodiment will be described.
In the sixth embodiment, in the time series calculation process, the section considering the change ψe calculated from the gear deflection angle and the tooth width meshing position is only a steady region where the gear rotation speed becomes a steady speed. And

  For example, in a region (transient state) that is not a steady region at a constant speed, such as during startup, a complicated response is shown due to the influence of inertial force due to startup acceleration, the characteristics of the drive motor, and the like. If the calculation is performed with the gear shape error added, the calculation takes time. Further, in this transitional state region, an operation such as image formation by driving the gear is not performed, so that it is not necessary to analyze in detail.

  For this reason, in the sixth embodiment, for example, at the initial stage of analysis such as at the time of start-up, calculation is performed with the inter-axis variation set to zero, and switching is performed slowly when the steady speed is reached. This shortens the calculation time.

FIG. 15 shows operations that are the contents of the time-series calculation process in the sixth embodiment.
In the time series calculation process in the sixth embodiment, as shown in FIG. 15, first, the initial time setting is set to t = 0 (step S31). Then, it is determined whether or not the minute time as one analysis step is a steady region (step S32). This determination may be made based on, for example, whether the rotational speed of the gear exceeds a predetermined threshold value, or may be determined based on whether the fluctuation range of the rotational speed of the gear is within a predetermined range. Thus, the determination as to whether or not the region is a steady region may use various predetermined determination methods.

  When it is determined that the region is a steady region, the differential equation in a minute time as one analysis step is solved similarly to the operation of the first embodiment described above (step S33), the data is stored, and the minute equation as the next analysis step is saved. Advance to time (steps S36, S37).

  If it is determined that the region is not a steady region, the change ψe due to the deviation angle and the tooth width meshing position described above is set to zero, and a differential equation in a minute time as one analysis step is solved (step S34). Then, the data is saved and the process proceeds to a minute time as the next analysis step (steps S36 and S37).

  As described above, in the sixth embodiment, in order to perform high-speed calculation, only the steady speed region is considered in the time series calculation process, and the influence of the declination is taken into consideration to improve the efficiency of analysis work. .

For this reason, in the sixth embodiment, in the time-series calculation process, the section in which the change ψe due to the deviation angle and the tooth width meshing position described above is considered is the only steady region. This simplifies the calculation when the behavior is complicated due to the inertial force and the influence of the drive motor in a transient state where the speed is not constant as at the time of startup. That is, it is possible to exclude the influence related to the calculation for considering the change ψe due to the deviation angle and the tooth width meshing position described above.
As a result, if there is no problem with the start time requiring a calculation time being excluded from the analysis target, the influence due to the change ψe due to the deviation angle and the tooth width meshing position is excluded, and high-speed calculation can be performed. For this reason, the efficiency of analysis work can be improved.

[Seventh Embodiment]
Next, a seventh embodiment will be described.
In the seventh embodiment, the gear transmission mechanism system including the analysis target gear is a driving gear transmission mechanism system for driving a photosensitive drum used for image formation in the image forming apparatus. For this reason, when outputting the operation result of the drive shaft and the driven shaft in the analysis result output step of step S8 in FIG. 1 described above, the output on the driven shaft is multiplied by the photosensitive member radius to obtain the characteristics on the surface of the photosensitive drum. It will be output after being converted to a value.

  In FIG. 16, a gear transmission mechanism system in which gears are combined is used as a driving gear transmission mechanism system for rotationally driving a cylindrical drum such as a photosensitive drum, a printing drum, or an image forming drum. An example of the configuration is shown.

  As shown in FIG. 16, in the power transmission mechanism 50 for rotating the photosensitive drum 55 as a rotating body, a motor 52 is attached to a side plate 51 serving as a base, and a drive gear 53 is attached to a drive shaft 52 a of the motor 52. Is attached. A driven gear 54 meshes with the drive gear 53, and the driven gear 54 is attached to a rotating shaft (driven shaft) 55a of the photosensitive drum 55. The rotating shaft 55a is rotatably supported by a gear bearing fixed to the side plate 51. In other words, in the power transmission mechanism 50, the rotating shaft (driven shaft) 55a is provided with the photosensitive drum 55 formed in a cylindrical shape that rotates together with the rotating shaft 55a.

  In the present embodiment, when performing an operation analysis process (gear design support process) on the power transmission mechanism 50 provided with the photosensitive drum 55 described above, first, any one of the first to sixth embodiments described above. Process by. Then, in the analysis result output process of step S8 in FIG. 1, the output of the driven shaft is multiplied by the radius of the photosensitive drum 55, and converted into a characteristic value on the surface of the photosensitive drum 55 and output. For this reason, the calculation result in the driven shaft calculated by the time series calculation process in step S6 in FIG. 1 is multiplied by the radius of the cylindrical drum to convert the characteristic value on the drum surface.

  For example, the positional deviation on the outer peripheral surface of the photosensitive drum 55 is obtained by multiplying the rotation angle error, which is the operation result of the driven gear 54 on the rotation shaft 55a, by the radius of the photosensitive drum 55. Similarly, the speed unevenness on the outer peripheral surface of the photosensitive drum 55 can be obtained by multiplying the rotational speed error, which is the operation result of the driven gear 54 on the rotary shaft 55a, by the radius of the photosensitive drum 55. The radius (that is, shape information) of the photosensitive drum 55 used for this conversion is set in the basic input process of step S1 in FIG.

  As described above, in the seventh embodiment, in the analysis result output process in step S8 of FIG. 1, the positional deviation on the surface of the photosensitive drum for one rotation period of each gear and the speed on the surface of the photosensitive drum for each gear meshing period. Output unevenness. The positional deviation and speed unevenness on the surface of the photosensitive member can be obtained by multiplying the angular transmission error or angular speed transmission error by the rotator radius. In particular, the surface position deviation in one rotation cycle tends to be output to paper as color misalignment in multi-color overwriting, and surface speed unevenness in the meshing cycle tends to be output as banding that causes density unevenness. Is very important for designers.

As described above, in the above-described seventh embodiment, the gear transmission mechanism system in which gears are combined is a gear transmission mechanism system that drives a cylindrical drum such as a photosensitive drum used for image formation.
Then, when outputting the operation results of the drive shaft and the driven shaft in the analysis result output step of step S8 in FIG. 1, the characteristic value on the surface of the cylindrical drum is obtained by multiplying the output of the driven shaft by the radius of the cylindrical drum. Convert to and output. For this reason, the calculation result in the driven shaft calculated by the time series calculation process in step S6 in FIG. 1 is multiplied by the radius of the cylindrical drum to convert the characteristic value on the drum surface.

  Therefore, according to the seventh embodiment described above, the gear support structure for rotating and supporting the gear in addition to the gear specification information and the gear shape error on the surface of the photosensitive drum 55 on which an image is actually formed. It is possible to obtain a relationship of characteristic values (positional deviation and speed unevenness) with respect to declination by the body and the bearing.

  As a result, the specifications information, drive condition information, material, and wear characteristics of the gear to be analyzed included in the gear transmission mechanism system are measured according to the positional deviation and the meshing period, which are characteristic values on the surface of the photosensitive drum 55. It is possible to predict whether or not the speed fluctuation will be affected. The positional deviation on the surface of the photosensitive drum 55 appears as a color deviation in multi-color superposition. Further, the speed fluctuation in the meshing cycle appears as banding that is density unevenness.

  Furthermore, in this embodiment, how much these characteristic values and contributions change during the wear evaluation time can be clarified in a short time by preliminary analysis. According to the present embodiment, in the analysis result output step of step S8 in FIG. 1, such analysis results can be output by various methods and presented to the user, and effective design support can be achieved.

[Eighth Embodiment]
Next, an eighth embodiment will be described.
In the eighth embodiment,
The gear transmission mechanism system that combines the gears described above is a gear transmission mechanism system for a roller that drives a transfer belt used for image formation in the image forming apparatus. Therefore, when outputting the operation result of the drive shaft and the driven shaft in the analysis result output step of step S8 in FIG. 1 described above, the output of the driven shaft is multiplied by the radius of the roller around which the transfer belt is wound, It is converted into a characteristic value on the transfer belt surface and output.

  FIG. 17 shows a configuration example when a gear transmission mechanism system in which gears are combined is used as a driving gear transmission mechanism system for rotationally driving a transfer belt 59 wound between a plurality of rollers. The transfer belt 59 is, for example, an intermediate transfer belt for overwriting a multicolor image.

As shown in FIG. 17, the transfer belt 59 for transferring image data is wound around and supported by a roller 57 and a roller 58. In the power transmission mechanism 60 for rotating the transfer belt 59, a motor 52 is attached to a side plate 51 serving as a base, and a drive gear 53 is attached to a drive shaft 52 a of the motor 52. A driven gear 54 meshes with the drive gear 53, and the driven gear 54 is attached to a rotating shaft (driven shaft) 57a of one roller 57. The rotating shaft 55a is rotatably supported by a gear bearing fixed to the side plate 51. The rotation shaft 58 a of the other roller 58 is also rotatably supported by a gear bearing fixed to the side plate 51.
That is, in the power transmission mechanism 60, the rotating shaft (driven shaft) 57a is provided with a roller 57 formed in a cylindrical shape that rotates together with the rotating shaft 57a.

  In this embodiment, when performing an operation analysis process (gear design support process) on the power transmission mechanism 60 provided with the transfer belt 59 described above, first, according to any of the first to sixth embodiments described above. Process. In the analysis result output process in step S8 in FIG. 1, the output of the driven shaft is multiplied by the radius of the roller 57, and converted into a characteristic value on the surface of the transfer belt 59 and output. For this reason, the calculation result of the driven shaft calculated by the time series calculation process of step S6 in FIG. 1 is multiplied by the radius of the roller 57 to convert the characteristic value on the surface of the transfer belt 59. The roller 57 is a roller to which the driven gear 54 in the gear transmission mechanism system is attached among the plurality of rollers around which the transfer belt 59 is wound. For this reason, the transfer belt 59 behaves according to the speed of the surface of the roller 57.

  As described above, in the eighth embodiment, in the analysis result output process of step S8 in FIG. 1, the positional deviation on the surface of the transfer belt 59 for each rotation period of each gear and the surface of the transfer belt 59 for each gear meshing period. Outputs uneven speed. The positional deviation and speed unevenness on the surface of the transfer belt 59 can be obtained in the same manner as in the fifth embodiment described above by multiplying the angle transmission error or angular speed transmission error by the radius of the roller 57. In particular, the surface position deviation in one rotation cycle tends to be output to paper as color misalignment in multi-color overwriting, and surface speed unevenness in the meshing cycle tends to be output as banding that causes density unevenness. Is very important for designers.

As described above, in the above-described eighth embodiment, the gear transmission mechanism system in which gears are combined is a gear transmission mechanism system for a roller that drives a transfer belt used for image formation.
Then, when outputting the operation results of the drive shaft and the driven shaft in the analysis result output step of step S8 in FIG. 1, the output of the driven shaft is multiplied by the roller radius and converted into a characteristic value on the belt surface and output. To do. For this reason, the calculation result of the driven shaft calculated by the time series calculation process of step S6 in FIG. 1 is multiplied by the radius of the roller 57 to convert the characteristic value on the surface of the transfer belt 59.

  Therefore, according to the above-described eighth embodiment, in addition to the gear specification information and the gear shape error on the surface of the transfer belt on which an image is actually formed, the gear support structure for rotating and supporting the gear, It is possible to obtain a relationship of characteristic values (positional deviation and speed unevenness) with respect to a deflection angle caused by a bearing.

  As a result, the specifications information, drive condition information, material, and wear characteristics, which are parameters of the gear transmission mechanism system, affect the positional deviation that is a characteristic value on the surface of the transfer belt 59 and the speed fluctuation in the meshing cycle. Or its contribution can be predicted. Note that the position shift on the surface of the transfer belt 59 appears as a color shift in multi-color superposition. Further, the speed fluctuation in the meshing cycle appears as banding that is density unevenness.

  Furthermore, in this embodiment, how much these characteristic values and contributions change during the wear evaluation time can be clarified in a short time by preliminary analysis. According to the present embodiment, in the analysis result output step of step S8 in FIG. 1, such analysis results can be output by various methods and presented to the user, and effective design support can be achieved.

  In the above-described eighth embodiment, the calculation result for the driven shaft calculated by the time series calculation step is multiplied by the radius of the roller 57 to convert it to a characteristic value on the surface of the transfer belt 59. Instead of this, the value obtained by adding the thickness of the transfer belt 59 to the radius of the roller 57 may be converted into a characteristic value on the surface of the transfer belt 59. By using such a calculation method, the characteristic value on the surface of the transfer belt 59 can be converted with high accuracy.

[Ninth Embodiment]
Next, a ninth embodiment will be described.
In the first to eighth embodiments described above, the gear design support method has been described. In the ninth embodiment, the gear design support device 1 is configured as shown in FIG. A case where each function in the embodiment is realized by a program will be described.

  The gear design support device 1 is configured using, for example, a computer system such as a known personal computer, and includes a CPU (Central Processing Unit) 2, a RAM (Random Access Memory) 3, a CRT (Cathode Ray Tube). ; Cathode Ray Tube) 4, keyboard 5, mouse 6, printer 7, data input unit 8, HDD I / F (Hard Disk Drive Interface) 31 Is done. These main parts are connected to each other by a bus 10.

  The CPU 2 performs comprehensive control in the gear design support device 1. The RAM 3 is a readable / writable memory that stores data used for control by the CPU 2. The CRT 4 is a display that displays information input from the keyboard 5 and the mouse 6, information indicating the analysis status, information indicating the analysis result, and the like. The keyboard 5 and the mouse 6 are well-known input devices, and mainly information related to a power transmission mechanism to be analyzed, a control command, and the like are input thereto. The printer 7 is of an electrophotographic type or an ink jet type, and outputs the processing result of the gear design support processing by the CPU 2, such as an analysis result, to a sheet.

  The data input unit 8 is, for example, various disk drives, and is an input unit that can read various information from a portable recording medium 11 such as a floppy disk (FD). In addition to this, the data input unit 8 may be an optical disk device or the like that can read various information from various optical disks as the recording medium 11.

  The HDD I / F 31 connects the HDD 32 as an external storage device to the bus 10, and can read an OS (Operating System) 20 and the gear design support program 21 according to the present embodiment from the HDD 32.

  In the recording medium 11 described above, various data set in the basic input process in step S1 of FIG. 1 described above are recorded for each gear constituting the gear transmission mechanism system to be analyzed in the apparatus 1. As a result, in the basic input step, the various data described above can be read from the recording medium 11 and set. That is, when the recording medium 11 is attached to the data input unit 8, reading by the CPU 2 becomes possible. In the present embodiment, not limited to this, for example, various data may be input from the keyboard 5 or the mouse 6, and the input form may be arbitrary.

  As described above, in the above-described ninth embodiment, the OS 20 that performs basic control of the CPU 2 and the gear design support program 21 according to the present embodiment are stored in an external storage device such as the HDD 32. Then, the OS 20 and the gear design support program 21 are read from the external storage device via the HDD I / F 31. Then, various data such as gear shape error data, eccentricity error data, and gear specification data are input using an input / output keyboard or mouse, or data on the recording medium 11 is read via the data input unit 8. As the recording medium 11, not only the floppy disk (registered trademark) described above but also a CD-ROM (Compact Disc Read Only Memory), a CD-R / RW (Compact Disc Recordable / ReWritable), a USB memory (Universal Serial Bus memory), for example. ) And the like can be used.

  By storing the gear design support program for executing the gear design support method in the first to eighth embodiments described above in the portable recording medium in this way, it is possible to carry and simulate in various places. Can be easily done.

  The gear design support program according to the present embodiment is installed in an information processing apparatus such as a computer, and the CPU of the apparatus performs processing, thereby realizing means for performing each process described in the first to eighth embodiments. For this reason, for example, the influence of design parameters, such as a gear specification, the rotation support structure of a gear, and a drive condition, can be predicted in advance by a short time analysis. Furthermore, a recording medium such as the HDD 32 can be brought into various places for simulation. For this reason, it is possible to provide a recording medium capable of providing gear design support with high accuracy and ease without checking the gear mechanism system for problems and eliminating the work of making a prototype and evaluating the gear drive system. .

For this reason, according to the ninth embodiment described above, it can be installed in various information processing apparatuses such as computers, and the influence of design parameters such as gear specifications, gear rotation support configuration, and driving conditions can be determined in advance and in a short time. Can be predicted by analysis of Also, simulation can be performed by bringing the recording medium to various places.
As a result, it is possible to provide a recording medium capable of supporting gear design with high accuracy and ease by eliminating the work of checking whether there is a problem with the gear mechanism system, making a prototype and evaluating the gear drive system.

[Tenth embodiment]
Next, a tenth embodiment will be described.
As shown in FIG. 19, the tenth embodiment shows a configuration example in which the HDD 32 in the ninth embodiment described above is an HDD 9 built in the apparatus 1.

  FIG. 19 is a block diagram showing a configuration example of the gear design support apparatus 1 according to this embodiment. The gear design support device 1 according to the present embodiment incorporates the HDD 32 according to the ninth embodiment as an HDD 9 instead of the HDD I / F 31 with the configuration shown in FIG.

  With such a configuration, by executing the gear design support program described in any of the first to eighth embodiments described above, information obtained from the dynamic analysis result of the gear over time, and information useful at the time of design can be obtained. Or from printed paper.

  As described above, according to the gear design support device 1 of the tenth embodiment described above, the CPU 2 performs the process by the gear design support program 21 to achieve any one of the first to eighth embodiments described above. Means for performing each of the described steps is realized.

  In the tenth embodiment described above, the influence of the design parameters such as the gear specifications, the rotation support configuration of the gear, and the driving conditions, which are design parameters affecting the rotation transmission characteristics of the gear and the gear excitation force, is reduced in advance. The purpose is to make predictions by analyzing time. At that time, the analysis is performed in consideration of the dynamic behavior due to the influence of the resonance phenomenon, the translational motion, the shaft deviated vibration, etc. as the influence of the inertia term and the rotational speed. Thus, there is provided a gear design support device capable of easily and accurately supporting gear design without checking the gear mechanism system for problems and eliminating the work of making and evaluating a gear drive system. For the purpose.

For this reason, the gear design support apparatus 1 of the tenth embodiment described above models the gear transmission mechanism system installed between the drive shaft and the driven shaft, and the dynamic behavior of the driven shaft with respect to the operation of the drive shaft. The gear design support apparatus for analyzing / calculating the above has the following means.
(1) Basic input means for receiving input of specification information which is a basic specification of the gear to be analyzed and target speed and driving torque drive condition information (2) Clearance between the shaft and the rotation shaft related to the bearing which supports the rotation of the gear Gear bearing information input means for receiving information on bearing spring stiffness, bearing damping coefficient (translation direction XYZ, rotation direction θz, declination direction θx, θy) (3) The basic input means and the gear bearing information input means Deflection amount calculation means to obtain the tangent (gear action line) corresponding to the rotation direction by obtaining information on the center circle center coordinates and the foundation circle radius of the sway, and to obtain the amount of deflection when the gears mesh on this tangent (4) Deflection amount The equation of motion for calculating the meshing force from the product of the tooth-to-tooth rigidity and generating the equation of motion for the tooth pair in contact with these forces on the gear action line (5) When solving Column calculating means (6) time series calculation means calculated drive shaft and an output means for outputting the operation result of the driven shaft

Then, the deflection amount calculation means obtains the deflection amount ψ as the sum of the five components ψa, ψb, ψc, ψd, and ψe. However,
ψa is the difference between the product of the gear rotation angle and the basic circle radius between the meshing gears ψb is the contact distance change ψc is the product of the drive side contact angle change and the drive side basic circle radius ψd is the driven The product of the change in the side contact angle and the driven side basic circle radius ψe is the change calculated from the deviation angle of the bearing and the tooth width meshing position.

  In this embodiment, gear translational motion and gear deflection motion, which are one of the factors that cause rotation unevenness, are incorporated into the analysis program, and the amount of change in deflection due to this translational motion and deflection motion is strictly calculated. For this reason, it becomes possible to analyze the dynamic behavior of a gear that performs rotational movement, translational movement, and declination while meshing.

As a result, the influence of design parameters such as gear specifications, gear rotation support configuration, and driving conditions, which influence the gear rotation transmission characteristics and gear vibration force, are predicted in advance and in a short time analysis. be able to. At that time, the analysis is performed considering dynamic behavior. This dynamic behavior is due to the influence of the inertial term and the rotational speed, such as the influence of resonance phenomenon, translational movement, and shaft deflection vibration.
As a result, it is possible to easily support the gear design with high accuracy without checking the gear mechanism system for problems and eliminating the work of making and evaluating the gear drive system.

  Each of the above-described embodiments is a preferred embodiment of the present invention, and the present invention is not limited to this, and various modifications can be made based on the technical idea of the present invention.

50, 60 Power transmission mechanism 51 Side plate 52 Motor 52a Drive shaft 53 Drive gear 54 Driven gear 55 Photoconductor drum 57, 58 Roller 55a, 57a Rotating shaft (driven shaft)
59 Transfer belt

JP 2012-43347 A

Claims (10)

In a gear design support method executed by a computer that models a gear transmission mechanism system provided on a drive shaft and a driven shaft and analyzes the dynamic behavior of the driven shaft with respect to the operation of the drive shaft,
A basic input process for receiving the specification information and driving condition information of the gear to be analyzed;
A gear bearing information input step for receiving input of information on a bearing that rotatably supports the gear;
Based on the input in the basic input step and the gear bearing information input step, a deflection amount calculating step for obtaining a deflection amount of the gear on the gear action line corresponding to the rotation direction between the meshing gears;
A motion equation deriving step of calculating a meshing force from the product of the deflection amount and the tooth pair rigidity, and generating a motion equation relating to the tooth pair contacting on the gear action line;
A time series calculation step for solving the equation of motion in time series,
In the deflection amount calculating step, the deflection amount is calculated as follows:
The difference between the product of the gear rotation angle and the base circle radius between the meshing gears;
Change of contact distance,
The product of the change in the drive side contact angle and the drive side basic circle radius,
The product of the change in the driven side contact angle and the driven side basic circle radius,
A gear design support method, characterized in that it is obtained as a sum of changes calculated from a deviation angle of a bearing portion and a tooth width meshing position.   2. The gear design support method according to claim 1, wherein, in the deflection amount calculation step, the deflection amount is obtained as a sum total obtained by further adding a deflection correction amount based on gear shape error information. In the time series calculation step,
When the product of the tooth width of the gear to be analyzed and the deviation angle of the bearing portion is larger than the gear shape error, a calculation including a change calculated from the deviation angle of the bearing portion and the tooth width meshing position is performed,
When the product of the tooth width of the gear to be analyzed and the deflection angle of the bearing portion is equal to or less than the gear shape error, the calculation is performed excluding the change calculated from the deviation angle and the tooth width meshing position of the bearing portion. The gear design support method according to claim 1 or 2, characterized by the above. In the time series calculation step,
When the bearing portion of the gear to be analyzed is a cantilever type, the calculation including the change calculated from the deflection angle and the tooth width meshing position of the bearing portion is performed,
The calculation is performed by excluding the change calculated from the deviation angle and the tooth width meshing position of the bearing portion when the bearing portion of the gear to be analyzed is a double-supported type. The gear design support method according to any one of the above.   5. The deviation angle of the change calculated from the deviation angle of the bearing portion and the tooth width meshing position is a deviation angle in a misalignment direction between the meshing gears. 6. Gear design support method. In the time series calculation step, it is determined whether or not the rotation speed of the gear is a steady region that is a steady speed,
For the time determined as a steady region by the determination, a calculation including a change calculated from the deflection angle of the bearing portion and the tooth width meshing position is performed,
6. The time determined by the determination as not being a steady region is calculated with a change calculated from a deviation angle and a tooth width meshing position of the bearing portion set to zero. The gear design support method according to Item 1. The gear transmission mechanism system is a transmission mechanism system for driving a drum used for image formation in an image forming apparatus,
It further includes a first analysis result output step of multiplying the calculation result of the driven shaft calculated by the time series calculation step by the radius of the drum and converting it to a characteristic value on the surface of the drum and outputting it. The gear design support method according to any one of claims 1 to 6, characterized in that: The gear transmission mechanism system is a transmission mechanism system for driving a transfer belt used for image formation in an image forming apparatus,
The transfer belt is supported by being wound around a plurality of rollers,
Multiply the calculation result of the driven shaft calculated by the time series calculation step by the radius of the roller to which the gear included in the gear transmission mechanism system is attached, and convert it to a characteristic value on the belt surface and output it. The gear design support method according to any one of claims 1 to 6, further comprising a second analysis result output step. In a gear design support program that models a gear transmission mechanism system provided on a drive shaft and a driven shaft and analyzes the dynamic behavior of the driven shaft with respect to the operation of the drive shaft,
A gear design support program that causes a computer to execute the gear design support method according to any one of claims 1 to 8. In the gear design support device that models the gear transmission mechanism system provided on the drive shaft and the driven shaft and analyzes the dynamic behavior of the driven shaft with respect to the operation of the drive shaft,
Basic input means for receiving the specification information and drive condition information of the gear to be analyzed;
Gear bearing information input means for receiving input of information on a bearing that rotatably supports the gear;
Deflection amount calculating means for obtaining a deflection amount of the gear on the gear action line corresponding to the rotation direction between the meshing gears based on the input by the basic input means and the gear bearing information input means;
A motion equation deriving means for calculating a meshing force from the product of the deflection amount and the tooth pair rigidity, and generating a motion equation relating to the tooth pair contacting on the gear action line;
A time series calculating means for solving the equation of motion in time series,
The deflection amount calculation means calculates the deflection amount.
The difference between the product of the gear rotation angle and the base circle radius between the meshing gears;
Change of contact distance,
The product of the change in the drive side contact angle and the drive side basic circle radius,
The product of the change in the driven side contact angle and the driven side basic circle radius,
A gear design support device characterized in that it is obtained as a sum of changes calculated from a deviation angle of a bearing portion and a tooth width meshing position.

Images