JPH11182638A - Transmission belt design support method of cylindrical rotating body drive system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To clarify the speed fluctuation of a cylindrical rotating body belt driving system by the quantity eccentricity of the cylindrical rotating body by calculating the disturbance torque by the gravity from the quantity of eccentricity of the rotation of the axis of the cylindrical rotating body and the rotational inertia moment, and achieving the model in for analysis so that the disturbance torque is applied to the axis of the cylindrical rotating body. SOLUTION: This disturbance torque due to the gravity is added to the torque load of a photosensitive drum as indicated in the basic equation of motion based on the formula of balance in each axis of rotation from the quantity of eccentricity of a photosensitive drum and its inertia mass. The speed fluctuation when the photosensitive drum is driven according to the magnitude of the inertia mass of the photosensitive drum and the quantity of eccentricity of a rotating body, can be understood. In the equation, ε is the difference the position of the center of gravity of the photosensitive drum and the position of the rotating body bearing, δ is the phase of the eccentricity, (g) is the acceleration of gravity, m2 is the mass of the photosensitive drum rotating body, J2' is the inertia moment (J2+m2.ε.ε) when the position of the center of gravity is eccentric, and J2 is the inertia moment around the axis of the photosensitive drum.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is applicable to a photosensitive drum of an image forming apparatus such as a copying machine or a laser printer, and a belt rotating system of a cylindrical rotating body of various automatic devices and home electric appliances. The present invention relates to a transmission belt design support method for a cylindrical rotating body drive system that analyzes the effects of shaft eccentricity, pulley shaft eccentricity, friction load, centrifugal force, etc., and optimizes the design.

[0002]

2. Description of the Related Art Conventionally, in an image forming apparatus using an electrophotographic process such as a copying machine or a laser printer, when a photosensitive drum on which an electrostatic latent image and a toner image are formed is driven, a drive output which is a motor shaft is used. It is common to use the power of the shaft at a reduced speed via a gear or a transmission belt. Among them, a belt drive system which is excellent in the degree of freedom in design layout, high speed, and transmission efficiency is widely used.

In general, a photosensitive member drive system is used in which the driving force of a drive motor is transmitted to a driven pulley provided on a drive shaft of a photosensitive drum via a drive pulley and a transmission belt. FIG. 1 shows a schematic configuration of a photoconductor driving system of the image forming apparatus.
FIG.

In FIG. 18, reference numeral 1 denotes a photosensitive drum on which an electrostatic latent image and a toner image are formed. Note that the photosensitive drum 1 is a cylindrical rotating body manufactured with component accuracy such as roundness and cylindricity. Reference numeral 2 denotes a drum drive motor having an encoder provided coaxially and serving as a drive source of the photosensitive drum 1,
3 is a drive pulley provided on the output shaft of the drum drive motor 2, 4 is a drum drive pulley (driven pulley) provided on the central axis of the photosensitive drum 1, 5 is a flywheel provided on the central axis of the photosensitive drum 1, Reference numeral 6 denotes a timing belt for transmitting the driving force of the driving pulley 3 to a drum driving pulley (driven pulley) 4. Reference numeral 7 denotes a polyurethane rubber made of, for example, a short and long blade having a thickness of 2 to 3 mm. A cleaning blade for bringing the edge portion into contact with the surface of the photosensitive drum 1 at a predetermined angle and a predetermined pressure to remove residual toner, paper dust, and the like after transfer on the photosensitive drum 1. Reference numeral 8 denotes an idler pulley which is normally provided on the slack side of the timing belt 6 and adjusts the slack of the belt.

Next, the basic operation of the photosensitive member drive system of the image forming apparatus having the above-described structure will be described. After charging, the photosensitive drum 1 scans in the main scanning direction of a laser optical unit (not shown) and receives a laser beam. A driving force that the drum drive motor 2 rotates and outputs is transmitted to the drum driving pulley (driven pulley) 4 of the photosensitive drum 1 via the timing belt 6 via the timing belt 6 so that the photosensitive drum 1 is driven at a constant speed at a predetermined speed. Rotate. Scanning in the sub-scanning direction is obtained by this constant speed rotation, and an electrostatic latent image of a surface image corresponding to the light irradiation is formed. Thereafter, the electrostatic latent image is developed, toner is adhered, and the electrostatic latent image is visualized. This toner image is transferred to a recording sheet, and further fixed and discharged. After the series of image forming processes, residual toner and the like after transfer adhere to the surface of the photosensitive drum 1 and are removed by the cleaning blade 7 to prepare for the next image forming process.
In this case, in particular, when the edge of the cleaning blade 7 is brought into contact with the photosensitive drum 7 as described above and rotated, the driving load (friction load) of the photosensitive drum 7 increases.

In general, when designing a drive system using a power transmission belt, a drive load, a belt tension, a pulley rotation speed, a belt speed, and a pulley diameter are taken into consideration, and the life and strength are mainly emphasized. The photosensitive drum 1 is precisely
When designing to drive, it relied on the experience of designers.

On the other hand, a flywheel 5 is mounted on the photosensitive drum 1 shaft by using one of the devices for rotating the photosensitive drum 1 at a constant speed, and a high-precision rotational drive is realized by utilizing the inertia effect. doing. After these drive mechanisms have been designed, the development of prototypes of them and the development of products, such as performing design tuning of the drive and its control system using actual machines, that is, evaluation of the actual machines, are underway.

Recently, demands for full-color and high-resolution copiers and laser printers have been increasing.
To achieve this, it is desired to improve driving accuracy such as color matching and to speed up design. In order to respond to such a demand, for example, as a design support method related to belt driving, a conventional technique of changing a belt spring according to a tension state and analyzing the spring is disclosed in Japanese Patent Application Laid-Open No. 7-226538. Supporting Method and Design Supporting Apparatus ".

[0009]

In the prior art as described above, a detailed modeling is performed with respect to the springiness applied to the transmission belt drive system. However, as described above, in the case of a photoconductor drive system such as a photoconductor drum that is driven to rotate at a constant speed, it is unlikely that the belt distortion changes from tension to compression, but rather the size changes in the tension region. Therefore, it is difficult to apply the model to such a photoconductor drive system.

[0010] Also, limited experience of designers (know-how)
However, in the development design using only the software, there is a problem that a designer's individual work load such as investigation and confirmation becomes large, and as a result, the development speed is slowed down. Furthermore, after the design is completed, a prototype is manufactured, and the tuning of the control system (e.g., gain investigation) is evaluated using the prototype. In other words, since the actual machine evaluation is performed by repeating trial and error until the optimization design is completed, there is a problem that the development period is prolonged and the development cost is increased due to an increase in the number of prototypes.

In particular, in the photoconductor drive system, internal / external fluctuations such as the effect of eccentricity of the photoconductor drum shaft and pulley (speed fluctuation) and the effect of frictional load on the surface of the photoconductor drum (speed fluctuation). It was necessary to perform model analysis and design in consideration of the factors.

The present invention has been made in view of the above, and clarifies various speed fluctuation factors exerted on a cylindrical rotating belt drive system such as a photosensitive drum by a model analysis, and provides an accurate guideline at the time of design. The purpose of the present invention is to shorten the design period and realize an analysis model that can be used as a mechanism model for control design.

[0013]

According to a first aspect of the present invention, there is provided a transmission belt design support method for a cylindrical rotary body drive system, wherein the cylindrical rotary body is driven via a transmission belt. A drive mechanism, wherein the drive mechanism is modeled, the behavior of the cylindrical rotating body axis with respect to the operation of the drive shaft is analyzed, and the result is reflected and supported in the design. A first step of calculating a disturbance torque due to gravity from the amount of eccentricity of the position of the center of gravity of the cylindrical rotating body axis and the moment of inertia of the cylindrical rotating body, and obtaining an analytical model for adding the disturbance torque to the torque load of the cylindrical rotating body axis And a second step of analyzing a speed variation of the cylindrical rotating body drive system according to the eccentric amount of the position of the center of gravity based on the analysis model.

That is, a disturbance torque due to gravity is calculated from the amount of rotation eccentricity of the shaft of the cylindrical rotating body and the moment of inertia of the rotating body, and this is modeled so as to be added to the shaft of the cylindrical rotating body, and analyzed, whereby the eccentricity of the cylindrical rotating shaft is obtained. The speed fluctuation of the cylindrical rotating body belt drive system due to the amount is clarified by analysis, and based on this result, the design support is performed.

According to a second aspect of the present invention, there is provided a driving mechanism for driving a cylindrical rotating body via a transmission belt, wherein the driving mechanism is modeled. In the method for supporting the design of the transmission belt of the cylindrical rotating body drive system, which analyzes the behavior of the cylindrical rotating body axis with respect to the operation of the drive shaft and reflects and supports the result in the design, the eccentricity of the driving pulley provided on the cylindrical rotating body axis A first step of obtaining an analysis model for changing the radius of the pulley according to the rotation angle of the drive pulley in consideration of the amount of rotation, and a step of driving the cylindrical rotating body drive system according to the amount of eccentricity of the drive pulley based on the analysis model. And a second step of analyzing a speed variation.

That is, by taking into account the amount of eccentricity of the driving pulley of the cylindrical rotating body shaft and modeling and analyzing the pulley radius in accordance with the driving pulley rotation angle, the amount of eccentricity of the pulley of the cylindrical rotating body shaft can be reduced. The effect (speed fluctuation) on the rotating belt drive system is clarified by analysis, and based on this result, design assistance is provided.

According to a third aspect of the present invention, there is provided a drive mechanism for driving a cylindrical rotating body via a power transmission belt, wherein the drive mechanism is modeled. A method for supporting the design of a transmission belt for a cylindrical rotating body drive system that analyzes the behavior of the cylindrical rotating body axis with respect to the operation of the drive shaft and reflects and supports the result in the design. A first step of obtaining an analytical model for varying a frictional load contacting the surface of the body, and a second step of analyzing a speed variation of the cylindrical rotating body drive system due to a deflection of the cylindrical rotating body based on the analytical model. And

That is, by modeling and analyzing the friction load in contact with the surface of the cylindrical rotator so as to fluctuate according to the amount of deflection of the surface of the cylindrical rotator, the contact portion corresponding to the deflection of the surface of the cylindrical rotator can be analyzed. The effect (speed fluctuation) of the friction load fluctuation on the cylindrical rotating body belt drive system is clarified by analysis, and based on the result, the design assistance is performed.

According to a fourth aspect of the present invention, there is provided a driving mechanism for driving a cylindrical rotating body via a transmission belt, wherein the driving mechanism is modeled. A method for supporting the design of a transmission belt for a cylindrical rotating body drive system that analyzes the behavior of the cylindrical rotating body axis with respect to the operation of the drive shaft and reflects and supports the result in the design. The centrifugal force generated by the imbalance is determined from the mass of the cylindrical rotor and the rotational speed of the cylindrical rotor, and the friction load in contact with the surface of the cylindrical rotor is varied according to the deformation of the support portion of the cylindrical rotor due to the centrifugal force. The method includes a first step of obtaining an analytical model and a second step of analyzing a speed fluctuation of the cylindrical rotating body drive system due to the centrifugal force based on the analytical model.

That is, the amount of deformation of the cylindrical rotator support member is determined from the centrifugal force generated by the eccentricity of the rotator of the cylindrical rotator shaft, and the modeling and analysis are performed so that the frictional load of the contact portion is changed according to the amount of deformation. In this way, the effect (speed fluctuation) of the friction load fluctuation of the contact part in response to the whirling caused by the centrifugal force on the cylindrical rotating body belt drive system is clarified by analysis, and based on this result, the design support is performed.

According to a fifth aspect of the present invention, there is provided a driving mechanism for driving a cylindrical rotating body via a transmission belt, wherein the driving mechanism is modeled. A method of supporting the design of a transmission belt for a cylindrical rotating body drive system that analyzes the behavior of the cylindrical rotating body axis with respect to the operation of the drive shaft and reflects and supports the result in the design. A disturbance torque due to gravity is calculated from a moment of inertia of the cylindrical rotating body, the disturbance torque is added to a torque load of the cylindrical rotating body shaft, and furthermore, a contact with a surface of the cylindrical rotating body is made in accordance with a deflection amount of the cylindrical rotating body. A first step of obtaining an analytical model for varying the frictional load, and a cylindrical rotating body drive system based on the eccentric amount of the position of the center of gravity and the deflection of the cylindrical rotating body based on the analytical model. A second step of analyzing the degree variation, is intended to include.

That is, by modeling and analyzing the gravitational disturbance torque due to the eccentricity of the axis of rotation of the cylindrical body and the fluctuation of the frictional load of the contact portion due to the run-out of the surface of the cylindrical body of rotation, the gravitational force due to the eccentricity is obtained. The effect (velocity fluctuation) on the cylindrical rotating body belt drive system caused by the fluctuation of the frictional load of the contact part due to the disturbance torque and the vibration of the cylindrical rotating body surface is clarified by analysis, and based on the results, the design assistance is performed.

According to a sixth aspect of the present invention, there is provided a driving mechanism for driving a cylindrical rotating body via a transmission belt, wherein the driving mechanism is modeled. A method for supporting the design of a transmission belt for a cylindrical rotating body drive system that analyzes the behavior of the cylindrical rotating body axis with respect to the operation of the drive shaft and reflects and supports the result in the design. The centrifugal force generated by the imbalance is determined from the mass of the cylindrical rotor and the rotational speed of the cylindrical rotor, and the friction load in contact with the surface of the cylindrical rotor is varied according to the deformation of the support part of the cylindrical rotor due to the centrifugal force. And calculating a disturbance torque due to gravity from the amount of eccentricity of the position of the center of gravity of the cylindrical rotating body shaft and the inertia moment of the cylindrical rotating body, and adding the disturbance torque to the torque load of the cylindrical rotating body shaft. A first step of obtaining an analytical model for varying a frictional load in contact with the surface of the cylindrical rotary body in accordance with the amount of deflection of the cylindrical rotary body; and a cylindrical rotary body drive system based on the centrifugal force based on the analytical model. And a second step of analyzing the speed fluctuation of the cylindrical rotating body drive system due to the eccentric amount of the position of the center of gravity and the deflection amount of the cylindrical rotating body.

That is, the gravitational disturbance torque due to the eccentricity of the shaft of the cylindrical rotating body, the frictional load fluctuation of the contacting part due to the vibration of the surface of the cylindrical rotating body, and the fluctuation of the frictional load of the contacting part due to the whirling of the centrifugal force are applied to the cylindrical rotating body shaft. By adding a model and analyzing it, the effect on the belt drive system of the cylindrical rotating body belt due to the frictional load fluctuation of the contact part due to the contact of the gravitational disturbance torque due to eccentricity, the vibration of the cylindrical rotating body surface and the centrifugal force (speed fluctuation) ) Is clarified by analysis, and based on this result, support is provided during design.

According to a seventh aspect of the present invention, the eccentricity of the shaft of the cylindrical rotating body is set at the center of the flywheel mounted on the shaft of the cylindrical rotating body. It is determined from the gap between the hole diameter and the shaft diameter of the cylindrical rotating body shaft.

That is, in calculating the amount of eccentricity of the cylindrical rotating body shaft, the amount of eccentricity of the cylindrical rotating body shaft is obtained by calculating from the gap between the mounting hole diameter of the flywheel attached to the cylindrical rotating body shaft and the shaft diameter of the cylindrical rotating body shaft. Can be easily calculated, and the work efficiency at the time of analysis when the shaft diameter tolerance is used as a parameter is improved.

Further, in the method for assisting the design of a transmission belt for a cylindrical rotating body drive system according to claim 8, the eccentricity of the driving pulley of the cylindrical rotating body is determined by the center hole diameter of the driving pulley and the cylindrical rotating body. It is determined from the gap between the shaft and the shaft diameter.

That is, in calculating the amount of eccentricity of the cylindrical rotary shaft pool, the cylindrical rotary body shaft pulley is obtained by determining from the gap between the mounting hole diameter of the pulley mounted on the cylindrical rotary shaft and the shaft diameter of the cylindrical rotary shaft. The amount of eccentricity can be easily calculated, and the work efficiency at the time of analysis when the shaft diameter tolerance is used as a parameter is improved.

According to a ninth aspect of the present invention, in the method for supporting the design of a transmission belt for a cylindrical rotating body drive system, when the analysis model is obtained, the contact angle of the transmission belt, the radius of the pulley, and the mass per unit length are used. The required belt inertial mass is added to the inertial mass of the cylindrical rotating body.

That is, by modeling the inertial mass of the belt obtained from the contact angle of the transmission belt, the pulley diameter, and the mass per unit length in addition to the inertial mass of the cylindrical rotating body, an analysis model taking the belt mass into account is taken into account. Is realized, the analysis accuracy is improved, and a remarkable effect is exhibited in a model having a large belt mass.

According to a tenth aspect of the present invention, the cylindrical rotating body is a photosensitive drum in an image forming apparatus.

That is, by applying the method for supporting the design of the transmission belt of the cylindrical rotating body drive system to the drive of the photosensitive drum in the image forming apparatus, an optimum load considering the load of the cleaning blade and the like which the photosensitive drum receives during image formation is considered. A drive system, that is, a high-speed and high-precision drive system is realized, and the color matching accuracy and resolution of a color image can be improved.
Furthermore, rotation unevenness in the sub-scanning direction such as jitter can be eliminated, and the design efficiency is improved.

[0033]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a driving system for a drive system of a cylindrical rotating body according to the present invention;
This will be described in detail. In this embodiment, a cylindrical rotating body to be driven will be described taking the above-described photosensitive drum as an example. In the embodiments described below,
The same components as those of the above-described conventional example are denoted by the same reference numerals as those of the above-described conventional example, and description thereof is omitted.

[Basic Model for Analysis] First, a basic model of each embodiment will be described. FIG. 1 is an explanatory diagram showing an analysis basic model (ideal model) of a transmission belt in the photoreceptor belt drive system according to the embodiment, which is an analysis model serving as a basis of each embodiment described later. First,
The illustrated symbols and the symbols of the equations of motion are listed.

(1) Drum drive motor part J1: Moment of inertia around motor axis θ1: Rotation angle of drive pulley 3 r1: Pulley radius of drive pulley 3 T1: Drive torque (2) Drum drive pulley part J2: Photosensitive drum Inertia moment around axis θ2: Rotation angle of drum drive pulley 4 r2: Pulley radius of drum drive pulley 4 (3) Idler pulley portion J3: Inertia moment of idler pulley 8 θ3: Rotation angle of idler pulley 8 r3: Idler pulley 8 (4) Belt spring model between motor shaft and photosensitive drum shaft k1: Rigidity c1: Viscosity (5) Belt spring model between photosensitive drum shaft and idler pulley shaft k2: Rigidity c2: Viscosity (6) Idler Spring model of belt between pulley shaft and motor shaft k3: rigidity c3: viscosity (6) Addition to photosensitive drum 1 Load F ₀ : static friction load _Fa : viscous load coefficient

In FIG. 1, an equation of motion is determined based on a balance equation for each rotation axis. Equation 1 shows the equation of motion in this basic model.

[0037]

(Equation 1)

Using the above equation of motion, the torque T required for driving and the rigidity k of the timing belt 7 required for this system
Is determined or given and designed while analyzing.

[Embodiment 1] Since the above-described model is an ideal model, a rotating body caused by a variation in component accuracy due to an actual tolerance (tolerance) in the drawing, a variation in assembly accuracy (stacking tolerance), and the like. Eccentricity is not taken into account. Therefore, when developing and designing a high-precision drive system, it is important to know in advance whether the effect of this eccentricity appears in the mechanism model as follows. Also, in the design of the control system, accurately modeling the mechanical system promotes the improvement of the accuracy in the control design.

Therefore, in the first embodiment, the effect (speed fluctuation) of the gravitational disturbance torque due to the eccentricity of one axis of the photosensitive drum on the photosensitive belt drive system is clarified by model analysis, and the design efficiency can be reduced. An example of providing a simple design support method will be described.

FIG. 2 is an explanatory diagram showing an analytical model of the transmission belt in the photosensitive belt drive system according to the first embodiment. The codes shown in the drawing and the codes of the equations of motion are listed as follows: ε: difference between the position of the center of gravity of the photosensitive drum 1 and the position of the bearing of the rotating body (the amount of eccentricity of the position of the center of gravity) δ: eccentric phase g: gravitational acceleration m2: Drum rotating body mass j2 ′: moment of inertia (= j2 + m2 · ε · ε) in which the position of the center of gravity is eccentric.

Here, first, a disturbance torque due to gravity is obtained from the amount of eccentricity of the photosensitive drum 1 and its inertial mass. Then, the disturbance torque is applied to the torque load of the photosensitive drum 1.

The equation of motion corresponding to the analysis model of FIG. Also, the response of the photosensitive belt drive system when a step input is given to the drum drive motor 2,
That is, FIG. 3 shows the analysis result of the photosensitive drum shaft angular velocity [rad / sec].

[0044]

(Equation 2)

As described above, by modeling and analyzing the photosensitive belt drive system in consideration of the influence of the eccentricity of the photosensitive drum 1 axis, the magnitude of the inertial mass of the photosensitive drum 1 and the eccentric amount of the rotating body are determined. It is possible to grasp the speed fluctuation amount when driven in response. Therefore, since it provides an accurate guideline at the time of design, the design period can be shortened, and can be applied as a mechanism model for control design.

[Embodiment 2] In this embodiment 2,
Analysis of the effect (speed fluctuation) of the eccentricity of the pulley of one axis of the photoconductor drum on the photoconductor belt drive system is clarified by analysis, and an example of realizing design support, shortening the development period, and applying control design to a mechanical model is described. .

The first embodiment is an analytical model in which the center of gravity of the photosensitive drum and the eccentricity of the rotating shaft (bearing) are taken into account. In the second embodiment, the center of gravity of the photosensitive drum coincides with the rotating shaft. However, this is an analysis model in the case where the drum drive pulley 4 to which the photosensitive drum shaft is attached is eccentric.

FIG. 4 is an explanatory diagram showing an analytical model of the transmission belt in the photosensitive belt drive system according to the second embodiment. Eps: the eccentricity of the drum driving pulley 4 of the photosensitive drum 1 ψa (2ra), ψb (2rb): the drum driving pulley 4
The other signs are the same as in the first embodiment.

As shown in FIG. 4, when the drum driving pulley 4 rotates, the radius r2 up to the timing belt 6 changes. Equation 3 shows the equation of motion corresponding to this analysis model. FIG. 5 shows the response of the photosensitive belt drive system (photosensitive drum shaft angular velocity [rad / sec]) and the drive motor shaft angular velocity [rad / sec] when a step input is given to the drum drive motor 2. Shown in

[0050]

(Equation 3)

The degree of influence of the eccentricity of the drum drive pulley 4 on the photosensitive drum 1 and the drive motor shaft can be grasped from the analysis model described above. Regardless of the eccentricity of the drum drive pulley 4, the speed fluctuation of the photosensitive drum 1 is suppressed by the flywheel effect (inertia effect), and the influence of the eccentricity of the pulley appears on the drum drive motor 2 side.

As described above, by making an analytical model and performing analysis, it is possible to grasp the amount of speed fluctuation when the drum driving pulley 4 attached to the photosensitive drum shaft is driven according to the amount of eccentricity. Therefore, it can provide an accurate guideline at the time of design, shortening the design period, and
It can also be applied as a mechanism model for control design.

[Embodiment 3] In this embodiment 3,
Analysis of the effect (speed fluctuation) on the photoconductor belt drive system due to the fluctuation of the frictional load of the contact portion (cleaning blade 7) in accordance with the fluctuation of the surface of the photoconductor drum 1 has been clarified by analysis, and the design support and the development period have been shortened. An example in which control design is applied to a mechanism model will be described.

Unnecessary substances such as residual toner and paper dust after transfer adhere to the surface of the photosensitive drum 1. As described above, the edge of the cleaning blade 7 is urged at a predetermined pressure in order to scrape off the attached unnecessary matter. At this time, if there is no surface fluctuation of the photosensitive drum 1, a constant friction load is applied. However, it is impossible to eliminate the run-out itself due to variations in component accuracy and variations after assembly. That is, although the magnitude of the run-out is different, it is inevitable that the friction load fluctuates.

This frictional force is obtained from the product of the coefficient of friction between the surface of the photosensitive drum 1 and the cleaning blade 7 and the resistance. The drag can be obtained from the rigidity and the amount of run-out of the sheet metal / spring supporting the cleaning blade 7.

FIG. 6 is an explanatory diagram showing an analysis model of the transmission belt in the photosensitive belt drive system according to the third embodiment. Of the symbols and the equations of motion shown in the drawing, εf: shake amount of the photosensitive drum 1 δf: phase of the shake amount kf: support rigidity of the cleaning blade 7 μ: friction coefficient between the surface of the photosensitive drum 1 and the cleaning blade 7 And the other symbols are the same as described above.

The equation of motion corresponding to this analysis model is as shown in Equation 4. In addition, as an effect of friction fluctuation due to the vibration of the photosensitive drum, an analysis result of a response (photosensitive drum shaft angular velocity [rad / sec]) of the photosensitive belt drive system when a step input is given to the drum drive motor 2 is shown. FIG.

[0058]

(Equation 4)

Incidentally, the smaller the coefficient of friction between the surface of the photosensitive drum 1 and the cleaning blade 7, the smaller the fluctuation component. Further, if the blade pressure of the cleaning blade 7 is set low, the fluctuation component can be reduced. However, when the friction coefficient and the blade pressure are reduced, the toner scraping force on the surface of the photosensitive drum 1, that is, the so-called cleaning property is reduced, and the residual toner cannot be completely removed. Is more likely to occur. For this reason, the allowable value of the amount of shake of the photosensitive drum 1 and the blade pressure are set while ensuring the cleaning quality. When designing in this way, it is possible to shorten the design development period by grasping the outline by analysis in advance.

[Fourth Embodiment] In the fourth embodiment,
When the photosensitive drum 1 oscillates due to the centrifugal force, the effect (speed variation) on the photosensitive belt drive system due to the friction load variation by the contact portion (cleaning blade 7) according to the whirling amount of the drum surface is clarified by analysis. This section describes an example of design support, shortening the development period, and applying control design to a mechanism model.

That is, when the rotation speed of the photosensitive drum 1 is increased in order to increase the speed of an image forming apparatus such as a copying machine or a laser printer, the centrifugal force due to the eccentricity of the photosensitive drum shaft increases as the square of the rotation speed. Become. Therefore, in the fourth embodiment, an analysis model considering the centrifugal force is realized.

More specifically, a dynamic shake amount due to the centrifugal force of the photosensitive drum is calculated from the rigidity supporting the photosensitive drum 1 and the mass, eccentricity, and rotation speed of the photosensitive drum, and modeled. FIG. 8 is an explanatory diagram showing an analysis model of the transmission belt in the photosensitive belt drive system according to the fourth embodiment. Ε: difference between the rotational center of gravity of the photosensitive drum 1 and the bearing of the rotating body (the amount of eccentricity of the center of gravity) δ: eccentric phase m2: photosensitive drum rotating body mass j2 ': Moment of inertia in which the position of the center of gravity is eccentric (= j2 + m2 ・ ε ・ ε) kf: Supporting rigidity of cleaning blade 7 kd: Supporting rigidity of photosensitive drum 1 μ: Coefficient of friction between photosensitive drum 1 surface and cleaning blade 7 is there. Other symbols are the same as described above.

The equation of motion derived from the analysis model shown in FIG.

[0064]

(Equation 5)

As an effect of the centrifugal force of the photosensitive drum at this time, analysis of the response (photosensitive drum shaft angular velocity [rad / sec]) of the photosensitive belt drive system when a step input is given to the drum drive motor 2 FIG. 9 shows the results.
As shown in FIG. 9, when the rigidity supporting the photosensitive drum 1 is low or when the rotation speed is increased, the effect of the centrifugal force is remarkable. Therefore, since it provides an accurate guideline at the time of design, the design period can be shortened, and can be applied as a mechanism model for control design.

[Fifth Embodiment] In the fifth embodiment,
Analysis of the influence (speed fluctuation) on the photoreceptor belt drive system due to the gravitational disturbance torque due to the eccentricity of the photoreceptor drum shaft and the frictional load fluctuation of the contact portion (cleaning blade 7) due to the fluctuation of the surface of the photoreceptor drum 1, This section describes an example of realizing design support, shortening the development period, and applying control design to a mechanism model.

That is, the fifth embodiment is a combination of the first and third embodiments described above, and is an analysis method when the photosensitive drum 1 is eccentric and the photosensitive drum surface oscillates. It is.

FIG. 10 is an explanatory diagram showing an analysis model of the transmission belt in the photosensitive belt drive system according to the fifth embodiment. Ε: difference between the rotational center of gravity of the photosensitive drum 1 and the bearing position of the rotating body (the amount of eccentricity of the center of gravity) δ: eccentric phase εf: the amount of vibration of the photosensitive drum 1 δf: phase of the amount of shake m2: mass of the rotating body of the photosensitive drum j2 ′: moment of inertia in which the position of the center of gravity is eccentric (= j2 + m2 ・ ε ・) kf: support rigidity of the cleaning blade 7 μ: surface of the photosensitive drum 1 and the cleaning blade It is the coefficient of friction with 7. Other symbols are the same as described above.

The equation of motion derived from the analysis model shown in FIG.

[0070]

(Equation 6)

At this time, as the influence of the friction fluctuation and the eccentricity of the position of the center of gravity caused by the vibration of the photosensitive drum, the response of the photosensitive belt drive system when a step input is given to the drum drive motor 2 (photosensitive drum shaft angular velocity [rad] /
[sec]) is shown in FIG.

Here, since the frictional fluctuation of the contact portion (cleaning blade 7) due to the vibration of the surface of the photosensitive drum 1 and the gravitational disturbance torque due to the eccentricity are modeled independently, an analysis in the case where the respective phases interfere with each other. This can be used as a design guideline and as a control design model.

FIG. 12 shows an evaluation example in which the analysis result and the measurement result are compared by changing the mass and inertia moment of the photosensitive drum rotating body depending on the size of the flywheel.
(A) shows the case where the flyhole is large, and (b) shows the case where the flyhole is small. From FIG. 12, the analysis value (graph with a cross) and the measurement value (graph with a solid line)
It can be seen that the results are almost the same. In other words, it is not necessary to perform each measurement by analysis, and it is possible to roughly verify the evaluation of the actual device based on the analysis result.

[Embodiment 6] The contact portion caused by the gravitational disturbance due to the eccentricity of the photosensitive drum shaft, the frictional change of the contact portion (cleaning blade 7) due to the luke and the shake of the photosensitive drum surface, and the swing around the centrifugal force. (Cleaning blade 7)
In this paper, we analyze the influence of the friction fluctuation of the photoreceptor on the photoreceptor belt drive system (speed fluctuation) by analysis, and describe an example of realizing the design support, shortening the development period, and applying the control design to the mechanism model.

That is, Embodiment 6 is a combination of Embodiments 4 and 5 described above, in which the photosensitive drum 1 is eccentric, the photosensitive drum surface has run-out, and the centrifugal force is reduced. This is an analysis model when it is necessary to consider the effects.

FIG. 13 is an explanatory diagram showing an analysis model of the transmission belt in the photosensitive belt drive system according to the sixth embodiment. Ε: difference between the rotational center of gravity of the photosensitive drum 1 and the bearing position of the rotating body (the amount of eccentricity of the center of gravity) δ: eccentric phase εf: the amount of vibration of the photosensitive drum 1 δf: phase of shake amount m2: mass of photosensitive drum rotating body j2 ′: moment of inertia with eccentric gravity center position (= j2 + m2 · ε · ε) kf: support rigidity of cleaning blade 7 kd: support rigidity of photosensitive drum 1 μ : Coefficient of friction between the surface of the photosensitive drum 1 and the cleaning blade 7 Other symbols are the same as described above.

The equation of motion derived from the analysis model of FIG. 13 is shown in Expression 7.

[0078]

(Equation 7)

At this time, the influence of the friction fluctuation due to the centrifugal force and the deflection and the eccentricity of the position of the center of gravity are considered as the effects of the drum driving motor
Of the photoconductor belt drive system when a step input is given to the photoconductor (photoconductor drum shaft angular velocity [rad / sec])
FIG. 14 shows the result of the analysis.

As described above, in the sixth embodiment, the fluctuation of the friction of the contact portion (cleaning blade 7) due to the fluctuation of the surface of the photosensitive drum + the fluctuation due to the centrifugal force and the gravitational disturbance torque due to the eccentricity are modeled independently. Therefore, analysis can be performed when the phases interfere with each other, and can be used as a design guideline and a control design model.

[Seventh Embodiment] In the seventh embodiment,
An example of calculating the amount of eccentricity, which is the displacement between the rotating body axis and the center of rotation, will be described.

Among the components constituting the photosensitive drum shaft portion, the flywheel 5 having the large mass and the moment of inertia has the greatest influence on the eccentricity. Therefore, the amount of eccentricity of the entire rotating body of the photosensitive drum can be substituted from the displacement of the center of gravity of the flywheel 5 and the axis of the rotating body. For example, in a certain copying machine, the flywheel 5 accounts for 70% of the mass of the photosensitive drum rotating body and about 90% of the moment of inertia.

An example of eccentricity of the flywheel 5 will be specifically described. FIG. 15 is an explanatory diagram showing a component configuration and an attached state of the flywheel 5. FIG. 15 (a)
As shown in FIG. 2, the flywheel 5 is provided with a mounting hole (diameter D), and the flywheel assembly reference shaft 10 to which the flywheel 5 is mounted has a convex portion (diameter d) provided on the photosensitive drum shaft. ing.

When the flywheel 5 is mounted on the flywheel assembly reference shaft 10, it is mounted while being held by hand. Therefore, as shown in FIG.
Since the upper side of the hole of the flywheel 5 and the upper side of the flywheel assembly reference shaft 10 are in contact with each other due to gravity, an eccentricity (gap) of (D−d) / 2 occurs (see the portion A). That is, the eccentricity of the entire photosensitive drum rotating body is ε =
(D−d) / 2.

The eccentricity can be obtained by calculating the hole diameter and the shaft diameter from drawing tolerances (fitting tolerances) at the time of design or by actually measuring them. However, measuring the eccentricity of the entire photosensitive drum rotating body requires a measuring device such as a balance correcting device, which is difficult without an actual machine. Therefore, the eccentricity of the photosensitive drum rotating body can be easily known by the above-described method.

[Eighth Embodiment] In the eighth embodiment,
An example of calculating the amount of eccentricity, which is the positional deviation between the photosensitive drum 1 and the drum driving pulley 4 attached to the photosensitive drum 1, will be described.

In the photosensitive belt drive system, a timing belt 6 and a pulley are used to transmit a torque to the photosensitive drum rotating body. As described above, when the pulley is eccentric as in the above-described second embodiment, it greatly affects the photosensitive belt driving system.

An example of eccentricity of the photosensitive drum 1 and the drum drive pulley 4 attached to the photosensitive drum 1 will be specifically described. FIG. 16 is an explanatory diagram showing a component configuration and an attached state of a photoconductor drum pulley portion. FIG. 16 (a)
As shown in FIG. 2, the photosensitive drum shaft 1a is provided with a mounting shaft (diameter dp), and the drum driving pulley 4 is provided with a mounting hole (diameter Dp).

When the drum driving pulley 4 is mounted on the photosensitive drum shaft 1a, it is mounted by hand. For this reason, as shown in FIG. 16B, the upper side of the hole of the drum driving pulley 4 and the photosensitive drum shaft 1a are caused by gravity.
Are in contact with each other, the amount of eccentricity is (Dp−dp) / 2
The amount of eccentricity (gap) occurs. That is, the eccentricity at the time of assembly is defined as the amount of eccentricity of the drum driving pulley 4, and εp = (Dp−
dp) / 2.

In addition, since the drum driving pulley 4 is formed by forming or the like on the basis of holes, the concentricity between the pitch circle (the pitch circle of the timing pulley) and the diameter of the mounting hole is high, and the eccentricity itself is small. However, since the eccentricity of the drum driving pulley 4 is caused by the gap between the shaft and the hole at the time of assembly, the amount of this gap is the amount of eccentricity. The amount of eccentricity can be easily obtained from the drawing tolerance (fitting tolerance) at the time of designing the hole diameter and the shaft diameter.

[Embodiment 9] In this embodiment 9,
An example of adding the belt mass to the pulley inertia mass, realizing an analysis that also considers the belt mass, and improving the analysis accuracy will be described.

There is no problem if the mass of the belt is smaller than the mass of the pulley or the rotating body, but if it becomes larger, it is necessary to perform modeling including the mass of the belt. Therefore, the portion of the timing belt 6 that is in contact with the pulley performs the same operation as the pulley, so that the contact length is added to the moment of inertia. This specific example will be described with reference to FIG.

In the figure, the timing belt 6 in section b
Since is free, it has been modeled as a spring that expands and contracts. Section a can be omitted when the mass of the belt itself is smaller than the moment of inertia of the pulley, but when the mass increases and the pulley radius increases, the moment of inertia of section a must be considered.

The belt mass of the contact portion is mbp, the radius of the pulley is rp, the moment of inertia of the core is Jp, and the contact angle is θ.
Assuming that p and the belt mass per unit length are mo, the moment of inertia jp ′ considering the belt contact portion is given by the following equation. Jp ′ = Jp + mbp · rp ² = Jp + mo · θp · rp ³

As described above, by modeling the belt mass and adding the model to the above-described analysis, the moment of inertia of the rotating body is approximated to an actual value, and accurate analysis can be performed.

[0096]

As described above, according to the power transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 1), the gravity is determined from the rotational eccentricity of the cylindrical rotating body shaft and the rotating body inertia moment. By calculating the disturbance torque caused by the rotation, modeling it so as to add it to the axis of the cylindrical rotating body, and analyzing it, the speed fluctuation of the cylindrical rotating body belt drive system due to the eccentricity of the cylindrical rotating body axis is clarified by the analysis. Since support is provided at the time of design based on the information, it provides an accurate guideline at the time of design, so that the design period can be shortened and can be applied as a mechanism model for control design.

Further, according to the power transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 2), the eccentricity of the driving pulley of the cylindrical rotating body shaft is taken into consideration, and the pulley is adjusted according to the driving pulley rotation angle. By modeling and analyzing to change the radius, the effect (speed fluctuation) of the pulley eccentricity of the cylindrical rotating body shaft on the cylindrical rotating body belt drive system was clarified by analysis. Since the support is provided, it provides an accurate guideline at the time of design, so that the design period can be shortened and can be applied as a mechanism model for control design.

According to the transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 3), the friction load in contact with the cylindrical rotating body surface is reduced in accordance with the amount of deflection of the cylindrical rotating body surface. By modeling and analyzing it to make it fluctuate, the effect (speed fluctuation) of the friction load fluctuation of the contact part on the belt driving system of the cylindrical rotating body due to the run-out of the surface of the cylindrical rotating body was clarified by analysis. Since support is provided at the time of design based on the information, it provides an accurate guideline at the time of design, so that the design period can be shortened and can be applied as a mechanism model for control design.

Further, according to the transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 4), the amount of deformation of the cylindrical rotating body supporting member is determined by the centrifugal force generated by the rotating body eccentricity of the cylindrical rotating body shaft. Is obtained, and the frictional load of the contact part is modeled so as to fluctuate according to the amount of deformation. The effects (speed fluctuations) are clarified by analysis, and based on this result, design assistance is provided. This provides an accurate guideline at design time, so that the design period can be shortened, and also as a control design mechanism model. Can be applied.

According to the power transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 5), the gravitational disturbance torque due to the eccentricity of the cylindrical rotating body shaft and the contact portion caused by the deflection of the cylindrical rotating body surface. By modeling and analyzing the fluctuation of the frictional load of the cylinder to be applied to the axis of rotation of the cylindrical body, the effect of the eccentricity on the gravitational disturbance torque and the fluctuation of the frictional load on the contact part due to the runout of the surface of the cylindrical body of rotation affects the belt drive system of the cylindrical body of rotation. The effects (speed fluctuations) are clarified by analysis, and based on this result, design assistance is provided. This provides an accurate guideline at design time, so that the design period can be shortened, and also as a control design mechanism model. Can be applied.

Further, according to the power transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 6), the gravitational disturbance torque due to the eccentricity of the cylindrical rotating body axis and the contact portion due to the deflection of the cylindrical rotating body surface. By modeling and analyzing the friction load fluctuation of the contact part and the fluctuation of the friction load of the contact part caused by the whirling of the centrifugal force, the gravitational disturbance torque due to the eccentricity, the vibration of the surface of the cylindrical rotating body and the centrifugal force are obtained by analyzing In order to clarify the effect (velocity fluctuation) of the friction load fluctuation of the contact part due to the touching of the contact part on the belt drive system of the cylindrical rotating body, and to provide assistance in the design based on this result, an accurate guideline in the design Therefore, the design period can be shortened, and it can be applied as a mechanism model for control design.

According to the transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 7), in calculating the eccentricity of the cylindrical rotating body axis, the flywheel attached to the cylindrical rotating body axis is attached. Since it is obtained from the gap between the hole diameter and the shaft diameter of the cylindrical rotating body shaft, the amount of eccentricity of the cylindrical rotating body shaft can be easily calculated, and the work efficiency at the time of analysis when the shaft diameter tolerance is used as a parameter is improved. .

Further, according to the transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 8), in calculating the eccentricity of the cylindrical rotating body shaft pool, the pulley attached to the cylindrical rotating body shaft is calculated. Since it is obtained from the gap between the mounting hole diameter and the shaft diameter of the cylindrical rotating body shaft, the amount of eccentricity of the cylindrical rotating body shaft pulley can be easily calculated, and the work efficiency at the time of analysis when the shaft diameter tolerance is used as a parameter is reduced. improves.

According to the transmission belt design support method for a cylindrical rotating body drive system according to the present invention (claim 9), the belt inertia mass obtained from the contact angle of the transmission belt, the pulley diameter and the mass per unit length. Is modeled in addition to the inertial mass of the rotating body of the cylinder, so that an analysis model that also takes into account the belt mass is realized, the analysis accuracy can be improved, and a remarkable effect is achieved in a model with a large belt mass.

Further, according to the driving belt design support method for a cylindrical rotating body drive system according to the present invention (claim 10), the driving belt design support method for a cylindrical rotating body drive system can be used to drive a photosensitive drum in an image forming apparatus. As a result, an optimal drive system that takes into account the load on the photosensitive drum during image formation, such as the cleaning blade, is realized, that is, a high-speed and high-precision drive system, improving color matching accuracy and resolution of color images. This makes it possible to eliminate unevenness in rotation in the sub-scanning direction, such as jitter, and to improve the design efficiency.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram showing an analysis basic model (ideal model) of a transmission belt in a photosensitive belt drive system according to an embodiment.

FIG. 2 is an explanatory diagram showing an analytical model of a transmission belt in the photosensitive belt drive system according to the first embodiment.

FIG. 3 is a graph showing the influence (analysis result) of the center of gravity eccentricity according to the first embodiment.

FIG. 4 is an explanatory diagram showing an analysis model of a transmission belt in a photosensitive belt drive system according to a second embodiment.

FIG. 5 is a graph showing an influence (analysis result) of pulley eccentricity according to the second embodiment.

FIG. 6 is an explanatory diagram showing an analysis model of a transmission belt in a photosensitive belt drive system according to a third embodiment.

FIG. 7 is a graph showing an influence (analysis result) of friction fluctuation due to drum runout according to the third embodiment.

FIG. 8 is an explanatory diagram showing an analysis model of a transmission belt in a photosensitive belt drive system according to a fourth embodiment.

FIG. 9 is a graph showing an influence (analysis result) of a friction change due to a centrifugal force according to the fourth embodiment.

FIG. 10 is an explanatory diagram showing an analytical model of a transmission belt in a photosensitive belt drive system according to a fifth embodiment.

FIG. 11 is a graph showing the influence (analysis result) of friction fluctuation due to drum runout + center of gravity position eccentricity according to the fifth embodiment.

FIG. 12 is a graph showing an evaluation result obtained by comparing the analysis result and the measurement result according to the fifth embodiment, in which the mass and the inertia moment of the photosensitive drum rotating body are changed depending on the size of the flywheel. a) When the flyhole is large,
(B) shows the case where the flyhole is small.

FIG. 13 is an explanatory diagram showing an analytical model of a transmission belt in a photosensitive belt drive system according to a sixth embodiment.

FIG. 14 is a graph showing an influence (analysis result) of frictional fluctuation due to centrifugal force + drum runout and eccentricity of the center of gravity position according to the sixth embodiment.

FIG. 15 is an explanatory diagram showing a component configuration and an attached state of a flywheel according to a seventh embodiment.

FIG. 16 is an explanatory diagram showing a component configuration and an attached state of a photosensitive drum pulley portion according to an eighth embodiment.

FIG. 17 is an explanatory diagram showing mass modeling of a pulley contact portion of a belt according to the ninth embodiment.

FIG. 18 is an explanatory diagram illustrating a schematic configuration of a photoconductor driving system of the image forming apparatus.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 photosensitive drum 2 drum drive motor 3 drive pulley 4 drum drive pulley (driven belt) 5 flywheel 6 timing belt 7 cleaning blade 8 idler pulley 10 flywheel assembly reference shaft 1a photosensitive drum shaft

Claims (10)

[Claims] 1. A driving mechanism for driving a cylindrical rotating body via a transmission belt, wherein the driving mechanism is modeled, the behavior of the cylindrical rotating body with respect to the operation of the driving shaft is analyzed, and the result is reflected in the design. In the method for supporting a transmission belt of a cylindrical rotating body drive system to be supported, a disturbance torque due to gravity is calculated from an eccentric amount of a center of gravity position on the cylindrical rotating body axis and an inertia moment of the cylindrical rotating body, and the disturbance torque is converted into the cylindrical rotating body. A first step of obtaining an analytical model to be added to the torque load of the rotating body shaft, and a second step of analyzing a speed variation of the cylindrical rotating body drive system according to the eccentricity of the position of the center of gravity based on the analytical model; A drive belt design support method for a cylindrical rotating body drive system, comprising: 2. A drive mechanism for driving a cylindrical rotary body via a transmission belt, wherein the drive mechanism is modeled, the behavior of the cylindrical rotary body axis with respect to the operation of the drive shaft is analyzed, and the result is reflected in the design. · An analysis model for changing the pulley radius according to the rotation angle of the driving pulley in consideration of the amount of eccentricity of the driving pulley provided on the cylindrical rotating body axis in the method for supporting the transmission belt design of the cylindrical rotating body drive system to be supported. And a second step of analyzing a speed variation of the cylindrical rotary body drive system according to the amount of eccentricity of the drive pulley based on the analysis model. A drive belt transmission belt design support method. 3. A drive mechanism for driving a cylindrical rotary body via a transmission belt, wherein the drive mechanism is modeled, the behavior of the cylindrical rotary body with respect to the operation of the drive shaft is analyzed, and the result is reflected in the design. A first step of obtaining an analytical model for varying a frictional load contacting the surface of the cylindrical rotating body according to the amount of deflection of the cylindrical rotating body, in the transmission belt design supporting method for the cylindrical rotating body drive system to be supported; Analyzing a speed variation of the cylindrical rotating body drive system due to the amount of deflection of the cylindrical rotating body based on the analysis model. 4. A drive mechanism for driving a cylindrical rotary body via a transmission belt, wherein the drive mechanism is modeled, the behavior of the cylindrical rotary body with respect to the operation of the drive shaft is analyzed, and the result is reflected in the design. A method for supporting a transmission belt design of a driving system of a cylindrical rotating body to support, wherein a centrifugal force caused by imbalance is obtained from a rotational eccentricity of the cylindrical rotating body, a mass of the cylindrical rotating body, and a rotation speed of the cylindrical rotating body; A first step of obtaining an analytical model for varying a frictional load contacting the surface of the cylindrical rotating body in accordance with the amount of deformation of the support of the cylindrical rotating body due to centrifugal force; A second step of analyzing speed fluctuations of the rotating body drive system. A method for supporting the design of a transmission belt of a cylindrical rotating body drive system, the method comprising: 5. A drive mechanism for driving a cylindrical rotary body via a transmission belt, wherein the drive mechanism is modeled, the behavior of the cylindrical rotary body with respect to the operation of the drive shaft is analyzed, and the result is reflected in the design. In the method for supporting a transmission belt of a cylindrical rotating body drive system to be supported, a disturbance torque due to gravity is calculated from an eccentric amount of a center of gravity position on the cylindrical rotating body axis and an inertia moment of the cylindrical rotating body, and the disturbance torque is calculated by the cylindrical rotating body. A first step of obtaining an analytical model for varying a frictional load contacting the surface of the cylindrical rotating body in accordance with the amount of deflection of the cylindrical rotating body in addition to the torque load of the rotating body shaft;
Analyzing the eccentricity of the position of the center of gravity and the fluctuation of the speed of the cylindrical rotating body drive system due to the run-out amount of the cylindrical rotary body based on the analysis model. Power transmission belt design support method. 6. A drive mechanism for driving a cylindrical rotary body via a transmission belt, wherein the drive mechanism is modeled, the behavior of the cylindrical rotary body with respect to the operation of the drive shaft is analyzed, and the result is reflected in the design. A method for supporting a transmission belt design of a driving system of a cylindrical rotating body to support, wherein a centrifugal force caused by an imbalance is obtained from a rotational eccentricity of the cylindrical rotating body, a mass of the cylindrical rotating body, and a rotation speed of the cylindrical rotating body; The frictional load contacting the surface of the cylindrical rotator is varied according to the amount of deformation of the support of the cylindrical rotator due to the centrifugal force, and the eccentricity of the position of the center of gravity on the axis of the cylindrical rotator and the moment of inertia of the cylindrical rotator , A disturbance torque due to gravity is calculated from the calculated torque, the disturbance torque is added to the torque load on the shaft of the cylindrical rotating body, and the frictional contact with the surface of the cylindrical rotating body is made according to the amount of deflection of the cylindrical rotating body. A first step of obtaining an analytical model for varying the frictional load, a speed variation of the cylindrical rotating body drive system due to the centrifugal force based on the analytical model, an eccentric amount of the position of the center of gravity, and a deflection amount of the cylindrical rotating body. A second step of analyzing a speed fluctuation of the cylindrical rotating body drive system. 7. The amount of eccentricity of the cylindrical rotating body shaft is determined by a gap between a center hole diameter of a flywheel mounted on the cylindrical rotating body shaft and a shaft diameter of the cylindrical rotating body shaft. A method for designing a transmission belt for a cylindrical rotating body drive system according to any one of claims 1, 4, 5, and 6. 8. The cylinder according to claim 2, wherein the amount of eccentricity of the driving pulley of the cylindrical rotating body is obtained from a gap between a center hole diameter of the driving pulley and a shaft diameter of the cylindrical rotating body shaft. Transmission belt design support method for rotating body drive system. 9. The inertial mass of the cylindrical rotating body is obtained by adding a belt inertial mass obtained from a contact angle of a transmission belt, a pulley radius, and a mass per unit length when obtaining the analysis model. Item 7. A method for supporting the design of a transmission belt of a cylindrical rotating body drive system according to any one of Items 1 to 6. 10. The method according to claim 1, wherein the cylindrical rotating body is a photosensitive drum in an image forming apparatus.