JP2000039807A - Method for supporting drum rotating mechanism design - Google Patents

Abstract

PROBLEM TO BE SOLVED: To present the method for supporting the drum rotating mechanism design capable of precisely performing preliminary verification of the drum rotating mechanism for the photoreceptor drum or the like. SOLUTION: The photoreceptor drum rotating mechanism 1 is constituted so that the photoreceptor drum 2 is fixed on a driving shaft 3 and a driven pulley 4 and a flywheel 5 are fixed thereon. It is rotary-driven by a driving motor 8 through a timing belt 7 extended around between the driven pulley 4 and the driving pulley 6. On a surface of the photoreceptor drum 2, a cleaning blade 10 held in contact with the surface on the photoreceptor drum 2 with a specified pressure is disposed for applying the specific friction load torque to the rotation of the photoreceptor 2. In analysis of movement of the photoreceptor drum 2 with respect to the motion of the driving shaft 3, by defining the friction load torque originated from the friction at the rotating time of the photoreceptor drum 2 into the drum rotating mechanism analysis model and by defining the friction load torque at the rotation stop time of the photoreceptor drum 2 as zero, the friction load torque originated from the friction in company with the rotation is defined more realistically therefore a prior verification for the photoreceptor drum rotating mechanism 1 is more precisely performed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for supporting the design of a drum rotating mechanism, and more particularly to a method for preliminarily verifying a drum rotating mechanism such as a photosensitive drum using a transmission belt used in a copying machine or a printer. The present invention relates to a drum rotation mechanism design support method to be performed.

[0002]

2. Description of the Related Art Conventionally, in driving a photosensitive drum used in a copying machine, a printer, or the like, the power of a drive shaft, which is a motor shaft, is reduced by a transmission belt using gears and pulleys. In general, the photosensitive drum is transmitted to a drive shaft of the drum to rotationally drive the photosensitive drum.

When designing a transmission belt for such a photosensitive drum rotating mechanism, an external load, belt tension, pulley rotation speed, pulley rotation number, and the like are set so as to satisfy specifications such as the life, strength, and rotation accuracy of the transmission belt. Design in consideration of diameter and belt speed.

In order to verify in advance whether the designed mechanism satisfies the specifications of the rotating mechanism of the photosensitive drum, an analytical model of the conventionally designed rotating mechanism of the photosensitive drum is used to set an equation of motion, A load torque generated on the motor shaft is given to this equation of motion to evaluate the force, acceleration, speed, displacement, and the like applied to the drum rotating mechanism.

However, when the way of applying load torque and the drum rotating mechanism become complicated, a non-linear phenomenon appears, which may not be able to be expressed by the definition of each matrix of the set equation of motion.

Therefore, a belt design support method and a design support apparatus (see Japanese Patent Application Laid-Open No. 7-229439) have been proposed.

The belt design support method and the design support apparatus perform a vibration calculation using a vibration calculation model in the belt longitudinal direction of the transmission belt drive system to support the design of the belt. When performing the vibration calculation, when the strain applied to the first element modeled as a belt span portion as a spring becomes a tensile strain,
While the spring constant is used as the spring characteristic of the belt span portion, when the compression strain occurs, the spring constant is changed to a spring constant lower than the spring characteristic of the belt span portion.

According to this technique, when a phenomenon in which the belt tension cannot maintain the belt rigidity due to buckling with respect to the compressive load is modeled and calculated by the equation of motion, the compressive load can be calculated as a small load. It is possible to calculate a state close to an actual phenomenon.

[0009]

However, such a conventional design support method does not consider the case where a frictional load torque is generated by contact with a drum, and the photosensitive drum and the like are not considered. Thus, when the cleaning blade for cleaning the photosensitive drum contacts the photosensitive drum to generate a frictional load torque, the design support of the drum rotation drive mechanism cannot be appropriately performed, and these rotary drum drive mechanisms cannot be provided. There is a need for a method of supporting the design of a computer. There is also a need for a method that supports the design of a drum rotation drive mechanism that takes into account the eccentricity of the drum due to the movement of the drive shaft of the drum.

Therefore, the invention according to claim 1 models a drum rotation mechanism for rotating the drum by rotating the drive shaft, and analyzes the behavior of the drum with respect to the operation of the drive shaft. When defining the friction load torque generated from the drum rotation mechanism analysis model, by defining the friction load torque when the rotation of the drum is stopped to zero, the constant friction load torque generated by the friction accompanying rotation becomes more realistic. It is an object of the present invention to provide a drum rotation mechanism design support method capable of performing more accurate and more accurate verification of a drum rotation mechanism in advance.

According to a second aspect of the present invention, the friction load torque data is defined in advance in association with a load torque other than the friction load torque acting on the drum, and when the behavior of the drum is analyzed, the data is calculated. By determining the value of the friction load torque with reference to the defined data on the way, it works to stop the rotation while the maximum friction torque is not reached, and when the maximum friction torque is reached, The friction load torque acting in the opposite direction is defined in advance in accordance with the characteristics of the friction load torque, and is modeled more realistically, so that the preliminary verification of the drum rotating mechanism can be performed more accurately and more accurately. It is an object of the present invention to provide a drum rotation mechanism design support method that can be performed.

According to a third aspect of the present invention, the friction load torque data is defined in association with a predetermined angular velocity of the drum, and when the behavior of the drum is analyzed, the defined data is referred to during the calculation. By determining the value of the frictional load torque, if the frictional load torque is large with respect to a slight change in the angle of the drive shaft of the drum, the frictional load torque reaches the maximum frictional load torque immediately after the start of rotation. In this case, if the friction load torque is suddenly changed from "0" to the maximum friction load torque, the system of the analysis model changes rapidly, and it becomes difficult to stably solve the convergence calculation and the like. To be able to smoothly change the load torque, suppress sudden changes in the analysis model system, shorten the calculation time, and perform accurate and quick verification of the drum rotation mechanism in advance. And its object is to provide a drum rotation mechanism design support method capable.

According to a fourth aspect of the present invention, when a drum rotation mechanism for rotating a drum by driving a drive shaft is modeled to analyze the behavior of the drum with respect to the operation of the drive shaft, the drum eccentricity and the mass are used. In order to analyze the behavior of the drum by modeling the calculated gravitational disturbance torque by adding it to the drive shaft, the eccentricity of the drum due to the deformation of the drive shaft and the drum due to the centrifugal force generated by the eccentricity, mass and angular velocity of the drum By calculating the change in the position at predetermined minute time intervals and modeling the drum rotation mechanism, based on the eccentricity corrected according to the deformation of the drive shaft due to centrifugal force, the gravity disturbance torque is obtained, To provide a drum rotation mechanism design support method capable of performing more accurate and more accurate preliminary verification of a drum rotation mechanism That.

According to a fifth aspect of the present invention, when a drum rotation mechanism for rotating the drum by driving the drive shaft is modeled and the behavior of the drum with respect to the operation of the drive shaft is analyzed, the drum eccentricity and the mass are used. Modeling the calculated gravitational disturbance torque by adding it to the drive shaft, and analyzing the behavior of the drum, the amount of eccentricity of the drum, the centrifugal force generated by the mass and angular velocity, and the pressure due to a predetermined contact object that contacts the drum The change in the position of the eccentricity of the drum due to the deformation of the drive shaft and the drum is calculated at every predetermined minute time interval, and the drum rotation mechanism is modeled. Based on the amount of eccentricity of the drum corrected according to the deformation of the drive shaft and the drum, the gravitational disturbance torque is obtained, and the preliminary verification of the drum rotating mechanism is further improved And its object is to provide a high accuracy and a drum rotation mechanism design support method further can be performed more accurately.

According to a sixth aspect of the present invention, the amount of movement of the eccentricity of the drum due to the deformation of the drive shaft and the drum is obtained by a simple calculation based on the material dynamics. An object of the present invention is to provide a drum rotation mechanism design support method that can be solved by a simple calculation formula and can be analyzed at high speed without applying a calculation load.

According to a seventh aspect of the present invention, the amount of movement of the eccentricity of the drum due to the deformation of the drive shaft and the drum is obtained by an approximate calculation such as finite element analysis, so that the drive shaft and the drum have complicated shapes. Even when calculation by material mechanics is difficult, the amount of movement of the drum can be easily obtained by approximation calculation represented by finite element analysis, and the behavior of the drum rotation mechanism taking into account the deformation of the drive shaft is further improved. It is an object of the present invention to provide a drum rotation mechanism design support method that can be performed accurately and more accurately.

[0017]

According to a first aspect of the present invention, there is provided a drum rotation mechanism design support method, wherein a drum rotation mechanism for driving a drum to rotate by rotation of a drive shaft is modeled, and the drum is driven with respect to the operation of the drive shaft. A drum rotation mechanism design support method for analyzing the behavior of the drum rotation mechanism, wherein when defining a friction load torque generated from friction due to contact during rotation of the drum in the drum rotation mechanism analysis model, the friction when stopping rotation of the drum The above object is achieved by defining the load torque to be zero.

According to the above construction, a drum rotation mechanism for rotating the drum by rotating the drive shaft is modeled,
In the analysis of the behavior of the drum with respect to the operation of the drive shaft, when the friction load torque generated from the friction due to the contact when the drum rotates is defined in the drum rotation mechanism analysis model, the friction load torque when the rotation of the drum is stopped is defined as zero. Therefore, the constant friction load torque generated by the friction caused by the rotation can be more realistically defined, and the preliminary verification of the drum rotating mechanism can be performed more accurately and more accurately.

In this case, for example, as described in claim 2, the data of the friction load torque is defined in advance in association with a load torque other than the friction load torque acting on the rotation of the drum, When analyzing the behavior of the drum, the value of the friction load torque may be determined with reference to the data during the calculation.

According to the above configuration, the data of the friction load torque is defined in advance in association with the load torque other than the friction load torque acting on the drum, and when the behavior of the drum is analyzed, the data is calculated during the calculation. Since the value of the friction load torque is determined with reference to the defined data, while not reaching the maximum friction torque, it works to stop the rotation,
When the maximum friction torque is reached, a friction load torque acting in the opposite direction to the rotation direction can be pre-defined according to the characteristics of the friction load torque, and can be modeled more realistically. The pre-verification of the rotation mechanism can be performed more accurately and more accurately.

Further, for example, as described in claim 3, the data of the friction load torque is defined in association with a predetermined angular velocity of the drum, and when the behavior of the drum is analyzed, the calculation is performed. The value of the friction load torque may be determined on the way with reference to the data.

According to the above configuration, the friction load torque data is defined in association with the predefined angular velocity of the drum, and when analyzing the behavior of the drum, the data is referred to during the calculation. Since the value of the friction load torque is determined, if the friction load torque is large with respect to the slight change in the angle of the drive shaft of the drum, the friction load torque reaches the maximum friction load torque immediately after the start of rotation. In this case, when the friction load torque is suddenly changed from “0” to the maximum friction load torque, the system of the analysis model changes rapidly,
It is possible to smoothly change the friction load torque, which makes it difficult to stably solve convergence calculations, etc., and can suppress sudden changes in the analysis model system, shortening the calculation time. Thus, the preliminary verification of the drum rotating mechanism can be performed accurately and in a short time.

According to a fourth aspect of the present invention, there is provided a drum rotation mechanism design support method, comprising: modeling a drum rotation mechanism for driving a drum to rotate by rotation of a drive shaft; A drum rotation mechanism design support method for modeling the behavior of the drum by adding a gravitational disturbance torque calculated from the eccentricity and mass of the drum to the drive shaft, the eccentricity, mass and angular velocity of the drum Calculating the change in the position of the eccentricity of the drum due to the deformation of the drive shaft and the drum due to the centrifugal force generated at every predetermined minute time interval, and modeling the drum rotation mechanism, thereby achieving the above object. Have achieved.

According to the above configuration, a drum rotation mechanism for rotating the drum by rotating the drive shaft is modeled,
When analyzing the behavior of the drum with respect to the operation of the drive shaft, the turbulence of gravity calculated from the eccentricity and mass of the drum is added to the drive shaft and modeled to analyze the behavior of the drum. Changes in the eccentric position of the drum due to the deformation of the drive shaft and the drum due to the centrifugal force generated by the mass and angular velocity are calculated at predetermined minute time intervals, and the drum rotation mechanism is modeled. The gravitational disturbance torque can be obtained based on the eccentricity corrected in accordance with the deformation of the drive shaft, and the preliminary verification of the drum rotating mechanism can be performed more accurately and more accurately.

According to a fifth aspect of the present invention, there is provided a method for designing a drum rotating mechanism, the method comprising: modeling a drum rotating mechanism for rotating a drum by rotating a driving shaft, and analyzing the behavior of the drum with respect to the operation of the driving shaft. A drum rotation mechanism design support method for modeling the behavior of the drum by adding a gravitational disturbance torque calculated from the eccentricity and mass of the drum to the drive shaft, the eccentricity, mass and angular velocity of the drum The change of the eccentric position of the drum due to the deformation of the drive shaft and the drum is calculated for each predetermined minute time interval by the centrifugal force generated by the above and the pressure by a predetermined contact object that comes into contact with the drum. The above object is achieved by modeling the drum rotating mechanism.

According to the above construction, a drum rotation mechanism for driving the drum to rotate by the rotation of the drive shaft is modeled,
When analyzing the behavior of the drum with respect to the operation of the drive shaft, the gravitational disturbance torque calculated from the amount of eccentricity and mass of the drum is added to the drive shaft and modeled, and when analyzing the behavior of the drum, the amount of eccentricity of the drum, The centrifugal force generated by the mass and angular velocity, and the pressure by a predetermined contact object that comes into contact with the drum, calculate the change in the position of the eccentricity of the drum due to the deformation of the drive shaft and the drum every predetermined minute time interval. Since the drum rotation mechanism is modeled, the gravity disturbance torque can be obtained based on the eccentricity of the drum corrected according to the deformation of the drive shaft and the drum due to the centrifugal force and the contact pressure of the cleaning blade, etc. The pre-verification of the rotating mechanism can be performed more accurately and more accurately.

In each of the above cases, for example, the amount of eccentric movement of the drum due to deformation of the drive shaft and the drum may be obtained by a simple calculation based on material dynamics.

According to the above configuration, the amount of movement of the drum eccentricity due to the deformation of the drive shaft and the drum is obtained by a simple calculation based on the material dynamics. Therefore, the amount of movement of the eccentricity of the drum due to the deformation of the drive shaft and the drum is simplified. It can be solved by a simple calculation formula and can be analyzed at high speed without applying a calculation load.

Further, for example, the amount of eccentric movement of the drum due to deformation of the drive shaft and the drum may be obtained by an approximate calculation such as a finite element analysis.

According to the above configuration, the amount of movement of the eccentricity of the drum due to the deformation of the drive shaft and the drum is obtained by an approximate calculation such as a finite element analysis. Even when calculation by dynamics is difficult, the amount of movement of the drum can be easily obtained by approximation calculation represented by finite element analysis, and the behavior of the drum rotation mechanism taking into account the deformation of the drive shaft can be further improved. It can be done better and more accurately.

[0031]

Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings. It should be noted that the embodiments described below are preferred embodiments of the present invention, and therefore, various technically preferable limitations are added. However, the scope of the present invention is not limited to the following description. The embodiments are not limited to these embodiments unless otherwise specified.

FIGS. 1 to 7 are diagrams showing a first embodiment of a drum rotation mechanism design support method according to the present invention. This embodiment corresponds to claims 1 to 3. is there.

FIG. 1 is a perspective view of a main part of a photosensitive drum rotating mechanism 1 to which a first embodiment of a drum rotating mechanism design support method according to the present invention is applied.

In FIG. 1, a photosensitive drum rotating mechanism (drum rotating mechanism) 1 is a rotating mechanism of a photosensitive drum 2 built in an electrophotographic copying machine or a printer.
The photoconductor drum 2 is fixed to a drive shaft 3. A driven pulley 4 and a flywheel 5 are fixed to the drive shaft 3, and the driven pulley 4 is driven to rotate by a timing belt 7 stretched between the driven pulley 4 and the drive pulley 6. The drive pulley 6 is connected and fixed to a motor shaft of the drive motor 8, and the drive motor 8 includes an encoder that detects the number of rotations or the rotation angle of the drive motor 8. An idler pulley 9 for applying a predetermined tension to the timing belt 7 is provided between the driving pulley 6 and the driven pulley 4.

A cleaning blade 10 is disposed on the surface of the photosensitive drum 2 in a state of contact with a predetermined pressure. The cleaning blade 10 is, as described later, mounted on the surface of the photosensitive drum 2 after the transfer. The photosensitive drum 2 is cleaned by scraping off the residual toner remaining on the photosensitive drum 2. Therefore, the photosensitive drum 2 receives a predetermined friction load torque with respect to its rotation by the cleaning blade 10.

The photosensitive drum rotating mechanism 1 includes a drive motor 8
, The driven pulley 6 is rotated, the driven pulley 6 is rotated and the driven pulley 4 is synchronously driven via the timing belt 7, and the driven pulley 4 is rotated to rotate the photosensitive drum 2. Then, the photosensitive drum rotating mechanism 1 stably rotates the photosensitive drum 2 by the inertia effect of the flywheel 5, and rotates the photosensitive drum 2 at a constant speed.

The rotating photosensitive drum 2 includes:
A laser beam modulated with image data is scanned and irradiated in the main scanning direction by an optical unit (not shown) to form an electrostatic latent image, and a developing device (not shown) is formed on the surface of the photosensitive drum 2 on which the electrostatic latent image is formed. The toner, which is a developer, is adhered by the unit and developed. When the photosensitive drum 2 developed with the toner is rotated and faces the transfer unit, the toner on the surface is transferred to the transfer paper (recording paper) by the transfer unit, and the photosensitive body 2 on which the toner transfer is completed is
The residual toner is removed by the cleaning blade 10 and is again used for forming an electrostatic latent image. The transfer paper on which the toner image has been transferred is conveyed to a fixing unit (not shown), and is heated and pressed by the fixing unit, so that the toner image is fixed on the transfer paper.

FIG. 2 is a conceptual diagram of a drum rotation mechanism model M1 in which the photosensitive drum rotation mechanism 1 is analytically modeled. In FIG. 2, J1 is the moment of inertia around the drive shaft of the drive motor 8, θ1 is the rotation angle of the drive shaft, r1
Is the radius of the driving pulley 6, T1 is the driving torque, J2
Is the moment of inertia of the photosensitive drum 2 around the drive shaft 3; θ2 is the rotation angle of the photosensitive drum 2; r2 is the radius of the driven pulley 4; J3 is the moment of inertia around the axis of the idler pulley 9; Is the rotation angle of the idler pulley 9, r
3 is the radius of the idler pulley 9 and k1 is the drive motor 8
Of the spring model of the timing belt 7 between the motor shaft of the photosensitive drum 2 and the drive shaft 3 of the photosensitive drum 2, c1 is the viscosity of the spring model, and k2 is the timing belt between the drive shaft 3 and the shaft of the idler pulley 9. 7, the rigidity of the spring model, c2
Is the viscosity of the spring model, and k3 is the idler pulley 9
, The rigidity of the spring model of the timing belt 7 between the shaft of the drive motor 8 and c3 is the viscosity of the spring model, F is the load (friction load) applied to the photosensitive drum 2 by the cleaning blade 10, The load F includes a static friction load Fo and a viscous load Fa.

Based on the drum rotation mechanism model M1, a motion equation 1 as shown in FIG. 3 can be created. In this motion equation 1, the symbols used are the symbols described above.

The equation of motion 1 is the same as the equation of motion created in the analysis model of the drum rotating mechanism, which has been performed in the past, and the equation of motion 1 alone gives the applied load torque as described above. However, there is a problem that a non-linear phenomenon appears due to an increase in the complexity of the drum rotation mechanism, and each matrix cannot be expressed by constants.

Therefore, in this embodiment, in the equation of motion 1, Fo acting as a frictional load torque of a portion corresponding to the load on the drive shaft 3 of the photosensitive drum 2 in the load vector on the right side is changed to a frictional load torque T. Then, a motion equation 2 as shown in FIG. 4 is created. When the angular velocity of the drive shaft 3 is “0” as the friction load torque T,
When T = 0 and the angular velocity of the drive shaft 3 is other than “0”, T = T
Set to give max. Here, Tmax is
This is the maximum friction load torque generated by friction.

That is, if the maximum frictional load torque Tmax is defined from the beginning as the frictional load torque T, the photosensitive drum 2 starts rotating even when no load torque is applied to the motor shaft of the drive motor 8 in a stopped state. Therefore, if the friction load torque T is defined in the load vector, a value of “0” is given when the rotation is stopped, and the maximum friction load torque Tmax is given at the start of the rotation, a contact object such as the cleaning blade 10 can be obtained. Can be modeled as a realistic model.

Now, assuming that the friction load torque T is a torque due to Coulomb friction, Tmax = μ
N × r. Where μ is the coefficient of friction, N is the contact pressure, r
Is the radius of the photosensitive drum 2.

With this setting, when the photosensitive drum 2 is stopped, the frictional load does not work, and the frictional load torque T generated by the cleaning blade 10 and the like is generated only after the rotation starts. The photosensitive drum rotating mechanism 1 can be realistically modeled, and the preliminary verification of the photosensitive drum rotating mechanism 1 can be performed more accurately and more accurately.

Further, as shown in FIG. 5, the frictional load torque T is set in advance in association with a load torque other than the frictional load torque T, and the frictional force is added to the photosensitive drum while referring to this data during the calculation. The friction load torque T is set by multiplying the radius by 2. By doing so, the friction load torque T
Until the maximum frictional load torque Tmax is reached, the photosensitive drum 2 can be modeled more appropriately so as to be in a stopped state, and the pre-verification of the drum rotating mechanism can be performed more accurately and more accurately. be able to.

Further, the friction load torque T may be set based on the force acting on the contact portion. In this case, as shown in FIG. The frictional force for the applied force is set in advance, and the frictional load torque T is set while referring to this data during the calculation. By doing so, the friction load torque T becomes the maximum friction load torque T
The model can be appropriately modeled so that the photosensitive drum 2 is in a stopped state until it reaches max.

As shown in FIG. 7, the frictional load torque T is preset in association with the drum angular velocity, that is, the angular velocity of the photosensitive drum 2, and the frictional load torque T is calculated while referring to this data during the calculation. Set. In this case, the friction load torque T becomes the maximum friction load torque Tmax.
Is reached, the photosensitive drum 2 can be appropriately modeled so as to be in a stopped state, and the preliminary verification of the drum rotating mechanism can be performed accurately and in a short time. In this case, the drum angular velocity may be converted to a linear velocity near the contact portion, and the friction load torque T may be set based on the linear velocity.

As described above, if the friction load torque T is large with respect to the slight change in the angle of the drive shaft 3 of the photosensitive drum 2, the friction load torque T reaches the maximum friction load torque immediately after the start of rotation. In this case, if the friction load torque T is suddenly changed from “0” to the maximum friction load torque, the system of the analysis model changes rapidly, and it is difficult to stably solve the convergence calculation and the like. In this case, as described above, if the friction load torque T is set in association with the drum angular velocity and the value of the friction load torque T is set by referring to this data during the calculation, the friction load torque T is changed smoothly. It is possible to suppress a sudden change in the system of the analysis model. As a result, the calculation time can be shortened, and the preliminary verification of the drum rotating mechanism can be performed accurately and in a short time.

FIG. 8 is a diagram showing a second embodiment of the method for supporting the design of a drum rotating mechanism according to the present invention. This embodiment corresponds to claims 4, 6 and 7 of the present invention. It is.

FIG. 8 is a front view of a main part of a photosensitive drum rotating mechanism 20 to which a second embodiment of the drum rotating mechanism design support method of the present invention is applied.

In FIG. 8, the photosensitive drum rotating mechanism 20
The photoconductor drum 21 is rotatably supported by a pair of bearings 23 and 24 via a rotation shaft 22 thereof.

As shown in FIG. 8, when the photosensitive drum 21 is rotating, the amount of eccentricity of the photosensitive drum 21 and the amount of rotation of the photosensitive drum 21 are varied due to variations in the fabrication of the photosensitive drum rotating mechanism 20 and assembly accuracy. The rotating shaft 22 and the photosensitive drum 21 are deformed by the centrifugal force caused by the above, and the center of gravity position of the photosensitive drum 21 is changed, that is, eccentric due to the deformation of the rotating shaft 22 and the photosensitive drum 21.

In order to analyze the behavior of the photosensitive drum rotating mechanism 20, in the present embodiment, the behavior of the photosensitive drum rotating mechanism 20 is calculated and analyzed for each minute time step which is a linear phenomenon. However, at this time, the gravitational disturbance torque is obtained based on the amount of eccentricity, the moment of inertia, and the mass of the photosensitive drum 21 with respect to the rotating shaft 22.

Here, the amount of eccentricity of the photosensitive drum 21 is determined by the amount of eccentricity of the photosensitive drum 21 due to the manufacturing variation and assembly accuracy of the actual photosensitive drum rotating mechanism 20, and the amount of eccentricity of the rotating shaft 22 and photosensitive member by centrifugal force. The amount of change in the eccentric position of the photosensitive drum 21 moved by the deformation of the drum 21;
The centrifugal force used at this time uses the value of the centrifugal force calculated one step before when calculating for each minute time step.

The centrifugal force is calculated from the eccentricity, angular velocity and weight of the photosensitive drum 21. The eccentricity and angular velocity used for calculating the centrifugal force are the same as the eccentricity calculated one step before. Use the value of angular velocity.

By doing so, the rotating shaft 2 due to the centrifugal force
2 and the gravitational disturbance torque can be calculated based on the eccentricity of the photoconductor drum 21 corrected by the deformation of the photoconductor drum 21.
Can be more accurately verified in advance.

The amount of eccentricity of the photosensitive drum 21 is
The amount of movement of the photosensitive drum 21 by material dynamics based on physical properties of the material of the rotating shaft 22 which is a component supporting the photosensitive drum 21, such as Young's modulus, Poisson's ratio, etc., and centrifugal force generated in the photosensitive drum 21. And the amount of movement may be used as the amount of eccentricity.

In this way, the amount of eccentricity of the photosensitive drum 21 can be calculated by a simple calculation formula, and the calculation load in the preliminary verification of the behavior of the photosensitive drum rotating mechanism 20 can be reduced.

Further, the amount of eccentricity of the photosensitive drum 21 is determined by the physical property value of the material of the rotating shaft 22, which is a component supporting the photosensitive drum 21, such as the Young's modulus and Poisson's ratio. As shown in FIG. 9, a model for approximation calculation represented by finite element analysis is created for the force and the photoconductor drum 21, and the movement amount of the photoconductor drum 21 is simulated based on the approximation calculation model. Alternatively, the simulated movement amount of the photosensitive drum 21 may be used as the eccentric amount.

In this way, even if the photosensitive drum 21 has a complicated shape and it is difficult to calculate by the material dynamics, the moving amount of the photosensitive drum 21 is calculated by an approximate calculation represented by a finite element analysis. , The amount of eccentricity of the photosensitive drum 21 is easily set, and the preliminary verification of the behavior of the drum rotating mechanism 20 in consideration of the deformation of the rotating shaft 22 and the photosensitive drum 21 is easily and accurately performed. Can be.

FIG. 10 is a diagram showing a third embodiment of the drum rotation mechanism design support method according to the present invention. This embodiment corresponds to claims 5 to 7.

FIG. 10 is a front view of a main part of a photosensitive drum rotating mechanism 30 to which a third embodiment of the drum rotating mechanism design support method of the present invention is applied.

In FIG. 10, the photosensitive drum rotating mechanism 3
Numeral 0 indicates that the photosensitive drum 31 is rotatably supported by a pair of bearings 33 and 34 via a rotation shaft 32 thereof.
A contact object 35 such as a cleaning blade is pressed against the photosensitive drum 31 with a predetermined pressing force.

As shown in FIG. 10, during the rotation operation of the photosensitive drum 31, the eccentricity of the photosensitive drum 31 and the rotation of the photosensitive drum 31 due to variations in the fabrication of the photosensitive drum drum rotating mechanism 30 and the assembly accuracy. The rotating shaft 32 is deformed by the centrifugal force and the pressing force of the contact object 35, and the eccentricity of the rotating shaft 32 changes the position of the center of gravity of the photosensitive drum 31.

In order to analyze the behavior of the photosensitive drum rotating mechanism 30, in the present embodiment, the behavior of the photosensitive drum rotating mechanism 30 is calculated and analyzed for each minute time step which is a linear phenomenon. At this time, the gravitational disturbance torque is obtained based on the amount of eccentricity, moment of inertia, and mass of the photosensitive drum 31 with respect to the rotating shaft 32.

Here, the amount of eccentricity of the photosensitive drum 31 is determined by the actual eccentricity of the photosensitive drum rotating mechanism 30 and the centrifugal force and the pressing force of the contact object 35 due to the manufacturing variation and assembly accuracy of the photosensitive drum rotating mechanism 30. And the amount of change in the position of the eccentricity of the photosensitive drum 31 moved by the deformation of the rotating shaft 32 and the photosensitive drum 31 due to the above, and the centrifugal force used at this time is calculated in each of the above minute time steps. The value of the centrifugal force calculated one step before is used.

The centrifugal force is calculated from the eccentricity, angular velocity and weight of the photosensitive drum 31, and the eccentricity and angular velocity used for calculating the centrifugal force are the same as the eccentricity calculated one step before. Use the value of angular velocity.

Thus, the photosensitive drum 3 corrected by the deformation of the rotating shaft 32 and the photosensitive drum 31 by the centrifugal force and the pressing force of the contact object 35 such as the cleaning blade.
The gravitational disturbance torque can be calculated based on the eccentric amount of 1, and the pre-verification of the behavior of the photosensitive drum rotating mechanism 30 can be performed more accurately only by the linear phenomenon.

The eccentricity of the photosensitive drum 31 is
As in the above-described embodiment, the movement amount of the photosensitive drum 31 is calculated by material dynamics based on the physical properties of the components of the photosensitive drum 31 such as Young's modulus and Poisson's ratio and the generated centrifugal force. However, this movement amount may be used as the eccentric amount.

In this way, the amount of eccentricity of the photosensitive drum 31 can be calculated by a simple calculation formula, and the calculation load in the preliminary verification of the behavior of the photosensitive drum rotating mechanism 30 can be reduced.

Further, the eccentricity of the photosensitive drum 31 is modeled as shown in FIG. 9 in the same manner as in the above-described embodiment, and an approximate calculation model represented by finite element analysis is produced. Then, the amount of eccentricity of the photosensitive drum 31 may be obtained.

In this way, even if the photosensitive drum 31 has a complicated shape and it is difficult to calculate by the material dynamics, the moving amount of the photosensitive drum 31 is calculated by an approximate calculation represented by a finite element analysis. Can be obtained, the amount of eccentricity of the photosensitive drum 31 can be easily set, and the behavior of the drum rotating mechanism 30 in consideration of the deformation of the rotating shaft 32 can be easily and accurately verified in advance.

Although the invention made by the present inventor has been specifically described based on the preferred embodiments, the present invention is not limited to the above, and various modifications can be made without departing from the gist of the invention. It goes without saying that it is possible.

For example, in each of the embodiments described above, the photosensitive drum is described as the drum, but the present invention is not limited to the photosensitive drum, and the drum is rotated by the rotation of the drive shaft. In general, the same applies as above.

[0075]

According to the drum rotation mechanism design support method of the present invention, a drum rotation mechanism for driving the drum to rotate by the rotation of the drive shaft is modeled, and the behavior of the drum with respect to the operation of the drive shaft is analyzed. When defining the friction load torque generated from the friction due to contact when the drum rotates in the drum rotation mechanism analysis model, the friction load torque when the rotation of the drum is stopped is defined as zero, so the friction load torque generated by the rotation Thus, the constant friction load torque can be more realistically defined, and the pre-verification of the drum rotation mechanism can be performed more accurately and more accurately.

According to the drum rotation mechanism design support method of the invention, the friction load torque data is defined in advance in association with a load torque other than the friction load torque acting on the drum, and When analyzing the behavior, the value of the friction load torque is determined with reference to the defined data in the middle of the calculation, so that the rotation stops while the maximum friction torque is not reached, When the frictional torque is reached, the frictional load torque that acts in the opposite direction to the rotation direction can be pre-defined according to the characteristics of the frictional load torque, and can be modeled more realistically. Pre-verification of the mechanism can be performed more accurately and more accurately.

According to the drum rotation mechanism design support method of the present invention, the friction load torque data is defined in association with the predefined angular velocity of the drum, and when analyzing the behavior of the drum, the data is defined. Since the value of the friction load torque is determined by referring to the defined data in the middle of the calculation, if the friction load torque is large with respect to the minute change in the angle of the drive shaft of the drum, the friction load torque is The torque reaches the maximum frictional load torque. In this case, if the frictional load torque is suddenly changed from “0” to the maximum frictional load torque, the system of the analysis model changes rapidly, and the convergence calculation and the like are stabilized. Difficulty in solving the problem is that the friction load torque can be changed smoothly, so that the system of the analytical model can be prevented from changing suddenly, the calculation time can be reduced, and the drum rotation can be reduced. It is possible to perform the pre-verification of the structure accurately and in a short period of time.

According to the drum rotation mechanism design support method of the invention, a drum rotation mechanism for rotating the drum by driving the drive shaft is modeled to analyze the behavior of the drum with respect to the operation of the drive shaft. The gravitational disturbance torque calculated from the eccentricity and mass of the drum is modeled by adding the torque to the drive shaft, and in order to analyze the behavior of the drum, the drive shaft and the centrifugal force generated by the eccentricity, mass and angular velocity of the drum The drum rotation mechanism is modeled by calculating the change in the position of the eccentricity of the drum due to the deformation of the drum at each predetermined minute time interval, so the eccentricity corrected according to the deformation of the drive shaft due to centrifugal force On the basis of,
The gravity disturbance torque can be obtained, and the preliminary verification of the drum rotating mechanism can be performed with higher accuracy and more accuracy.

According to the drum rotation mechanism design support method of the present invention, when the drum rotation mechanism that drives the drum to rotate by the rotation of the drive shaft is modeled, the behavior of the drum with respect to the operation of the drive shaft is analyzed. When modeling the behavior of the drum by adding the turbulence torque calculated from the eccentricity and mass of the drum to the drive shaft, and analyzing the behavior of the drum,
The change in the position of the eccentricity of the drum due to the deformation of the drive shaft and the drum due to the centrifugal force generated by the amount of eccentricity, mass and angular velocity of the drum, and the pressure by a predetermined contact object that contacts the drum, is determined by a predetermined minute time interval. Since the drum rotation mechanism is modeled by calculating each time, the gravity disturbance torque is calculated based on the eccentricity of the drum corrected according to the deformation of the drive shaft and the drum due to the centrifugal force and the contact pressure of the cleaning blade and the like. Thus, preliminary verification of the drum rotation mechanism can be performed with higher accuracy and more accuracy.

According to the drum rotation mechanism design support method of the present invention, the amount of movement of the eccentricity of the drum due to the deformation of the drive shaft and the drum is obtained by a simple calculation based on the material dynamics. The displacement of the eccentricity of the drum due to the deformation can be solved by a simple calculation formula, and the analysis can be performed at high speed without applying a calculation load.

According to the drum rotation mechanism design support method of the present invention, the amount of movement of the eccentricity of the drum due to the deformation of the drive shaft and the drum is obtained by an approximate calculation such as finite element analysis. Even if the calculation is difficult due to the material dynamics due to the complicated shape of the drum or the drum, the amount of movement of the drum can be easily obtained by the approximate calculation represented by the finite element analysis. The behavior of the drum rotation mechanism considered can be performed with higher accuracy and more accuracy.

[Brief description of the drawings]

FIG. 1 is a perspective view of a main part of a photosensitive drum rotating mechanism to which a first embodiment of a drum rotating mechanism design support method of the present invention is applied.

FIG. 2 is a diagram showing a drum rotation mechanism model obtained by analytically modeling the photosensitive drum rotation mechanism of FIG.

FIG. 3 is a view showing a motion equation created based on the drum rotation mechanism model of FIG. 2;

FIG. 4 is a diagram showing a motion equation created by giving a friction load torque to the right side of the motion equation in FIG. 3;

FIG. 5 is a view showing a graph for setting a friction load torque in relation to a total of load torques other than friction.

FIG. 6 is a diagram showing a graph for setting a frictional load torque by setting a frictional force with respect to a force acting on a contact portion with respect to a total of forces other than a frictional force.

FIG. 7 is a diagram showing a graph for setting a friction load torque with respect to a drum angular velocity in advance and setting the friction load torque at the time of analysis;

FIG. 8 is a front view of a main part of a photosensitive drum rotating mechanism to which a second embodiment of the drum rotating mechanism design support method of the present invention is applied.

FIG. 9 is a diagram showing an approximate calculation model of the photosensitive drum rotating mechanism of FIG. 8;

FIG. 10 shows a third embodiment of the drum rotation mechanism design support method according to the present invention.
The principal part front view of the photoreceptor drum rotation mechanism to which the embodiment is applied.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 photoconductor drum rotation mechanism 2 photoconductor drum 3 drive shaft 4 driven pulley 5 flywheel 6 drive pulley 7 timing belt 8 drive motor 9 idler pulley 10 cleaning blade 20 photoconductor drum rotation mechanism 21 photoconductor drum 22 rotation shaft 23, 24 Bearing 30 Photoconductor drum rotation mechanism 31 Photoconductor drum 32 Rotation shaft 33, 34 Bearing 35 Contact object

Claims (7)

[Claims] 1. A drum rotation mechanism design support method for modeling a drum rotation mechanism for driving a drum to rotate by rotation of a drive shaft and analyzing a behavior of the drum with respect to an operation of the drive shaft. A friction load torque generated from friction due to contact sometimes defined in the drum rotation mechanism analysis model, wherein the friction load torque when the rotation of the drum is stopped is defined to be zero. 2. The method according to claim 1, wherein the data of the friction load torque is defined in advance in association with a load torque other than the friction load torque acting on the rotation of the drum. 2. The method according to claim 1, wherein the value of the friction load torque is determined with reference to the data on the way. 3. The friction load torque data is defined in association with a predetermined angular velocity of the drum, and when analyzing the behavior of the drum, the friction load torque is referred to during the calculation. 2. The method according to claim 1, wherein the torque value is determined. 4. A method of modeling a drum rotation mechanism for rotating a drum by rotating a drive shaft and analyzing a behavior of the drum with respect to an operation of the drive shaft, a gravity disturbance torque calculated from an eccentric amount and a mass of the drum. A drum rotation mechanism design support method for modeling the behavior of the drum by adding the model to the drive shaft, wherein the eccentricity of the drum, the centrifugal force generated by the mass and the angular velocity cause the drive shaft and the drum to A drum rotation mechanism design support method, wherein a change in the eccentric position of the drum due to deformation is calculated at predetermined small time intervals, and the drum rotation mechanism is modeled. 5. A model of a drum rotation mechanism for driving a drum to rotate by rotation of a drive shaft, and analyzing the behavior of the drum with respect to the operation of the drive shaft, the gravity disturbance torque calculated from the eccentricity and mass of the drum. A drum rotation mechanism design support method for modeling the behavior of the drum by adding the model to the drive shaft, wherein the centrifugal force generated by the eccentricity, mass and angular velocity of the drum and a predetermined The change in the eccentric position of the drum due to the deformation of the drive shaft and the drum due to the pressure by the contact object is calculated at predetermined minute time intervals to model the drum rotation mechanism. Drum rotation mechanism design support method. 6. The method according to claim 4, wherein an amount of eccentric movement of the drum due to deformation of the drive shaft and the drum is obtained by a simple calculation based on material mechanics. . 7. The method according to claim 4, wherein an amount of eccentric movement of the drum due to deformation of the drive shaft and the drum is obtained by an approximate calculation such as a finite element analysis.
The drum rotation mechanism design support method described in the above.