JP2003149065A - Friction measuring apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a friction measuring apparatus in which a vertical drag is generated between a rotor and a belt and in which a change in the vertical drag due to the deflection of the belt in its thickness direction can be excluded. SOLUTION: The friction measuring apparatus is provided with a rotor- surface-speed measuring part 3 which measures the surface speed of the driving rotor used to drive the belt, a belt-speed measuring part 4 which measures a belt speed, a rotor-load-torque measuring part 5 which measures a rotor load torque generated at the driving rotor, a frictional-force computing part 6 in which a frictional force generated between the driving rotor and the belt with reference to the speed difference between the surface speed and the belt speed is calculated on the basis of the measured surface speed, the measured belt speed and the measured rotor load torque and a belt tension generation part 7 which gives a load in the direction of gravity with reference to the belt. The measuring apparatus is provided with a measurement control part 21 which generates a recording finish signal used to finish the recording of measured results of the surface speed, the belt speed and the rotor load torque when the speed difference between the surface speed and the belt speed becomes a preset prescribed value or less.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a frictional force generated between a drum-shaped rotating body which constitutes an image forming apparatus such as a copying machine or a printer and a belt such as a transfer belt or a conveyor belt. The present invention relates to a friction measuring device for measuring.

[0002]

2. Description of the Related Art Conventionally, in order to measure a frictional force generated between a drum-shaped rotating body which constitutes an image forming apparatus such as a copying machine or a printer and a belt conveyed by the rotating body, With the rotating body kept stationary, a belt is pressed against the rotating body by applying a load to the belt from above the belt, and the belt is pulled in that state, and the pulling force is measured. Further, as disclosed in, for example, Japanese Patent Laid-Open No. 2000-25284, one of the clutches is fixed to the innermost shaft using an encoder and a clutch of a low friction member, and the other of the clutches is attached to the encoder. It is fixed and fixed to the pinch roller of the low friction member, and the surface speed of the pinch roller including slippage when the printing paper is passed (that is, the printing paper conveyance speed at this time) and this structure The frictional force was calculated from the speed difference between the surface speed of the pinch roller (passage speed of printing paper at this time) when the pinch roller without slippage of another system was passed. That is, in order to measure the frictional force between the rotating body and the belt by such a method, an unclosed (not ring-shaped) belt is passed instead of the printing paper.

[0003]

[Patent Document 1] Japanese Unexamined Patent Application Publication No.
In the above-mentioned method disclosed in Japanese Patent Application Publication No. 000-25284,
Since the position of the pinch roller is fixed, the normal force, which is one of the factors that determines the frictional force, fluctuates depending on the thickness of the belt, so that only the frictional force peculiar to the device can be evaluated. was there. Furthermore, if the belt to be measured has a runout in the thickness direction, the normal force also fluctuates, making it difficult to measure the correct frictional force. Further, for example, the transfer belt mounted on a copying machine or a laser printer is tensioned, and is mounted in a state of being stretched in the circumferential direction and contracted in the thickness direction,
To correctly measure the frictional force of such a transfer belt,
It is desirable to apply tension to the belt and measure the frictional force as in the actual machine. However, it is difficult to measure the frictional force in the state where the tension is generated in the belt in any of the above-mentioned conventional techniques. Further, for example, a transfer belt mounted on a copying machine or a laser printer and a roller that drives the transfer belt are in contact with each other with a winding angle on an actual machine, and when measuring the frictional force of these, It is desirable to measure the frictional force in the state of contact with the same wrap angle as on the actual machine. However, it is difficult to measure the frictional force while maintaining the winding angle in any of the above-mentioned conventional techniques. An object of the present invention is to solve such a problem of the related art. Specifically, when measuring the frictional force between the rotating body to be measured and the belt, the belt is desired to be the desired rotating body. The belt is wound at a winding angle, a desired predetermined tension is applied to the belt, and a vertical reaction force is generated between the rotating body and the belt by the predetermined tension to eliminate the fluctuation of the vertical reaction force due to the shake in the thickness direction. Another object of the present invention is to provide a friction measuring device capable of measuring a friction force in a short time by keeping a speed difference between a surface speed of a rotating body of the rotating body and a belt speed of the belt within a predetermined range.

[0004]

In order to solve the above-mentioned problems, in the invention described in claim 1, the surface speed and belt speed of the drive rotating body for driving the belt and the rotation generated in the drive rotating body. From a body load torque, in a friction measuring device for measuring a frictional force generated between the driving rotating body and the belt with respect to a speed difference between the surface speed and the belt speed,
A belt tension generating means for applying a load in the direction of gravity to the belt is provided. In the invention according to claim 2, in the invention according to claim 1, when the speed difference between the surface speed and the belt speed is equal to or less than a preset predetermined value, the surface speed, the belt speed, and the rotor load The measurement control means for generating a recording end signal for ending the recording of the torque measurement result is provided. According to the invention of claim 3,
In the invention described above, a belt end portion fixing means for uniformly fixing the end portion of the belt is provided, and the belt tension generating means is configured so that the weight is attached to the position of the center of gravity of the belt end portion fixing means. According to a fourth aspect of the present invention, in the first aspect of the present invention, the belt is formed in a ring shape, and a load that is inscribed in the belt and rotates below the drive rotating body together with the drive rotating body. Equipped with a rotating body for
The belt tension generating means is configured to generate tension on the belt by the weight of the load rotating body. According to a fifth aspect of the invention, in the first aspect of the invention, a contact angle changing rotary body that can move the position at least in the vertical direction is provided, and the position of the contact angle changing rotary body is changed. As a result, the contact angle of the belt with respect to the driving rotating body is changed. Also,
According to a sixth aspect of the present invention, in the first aspect of the present invention, an in-device load torque calculating means or an in-device load torque for calculating an in-device load torque that is generated other than a frictional force between the driving rotating body and the belt. An in-apparatus load torque input means for inputting a value and a frictional force correction means for subtracting the in-apparatus load torque from the rotating body load torque to correct the frictional force are provided. Further, in the invention according to claim 7, in the invention according to claim 6, the rotating body load torque when the speed difference between the surface speed and the belt speed is equal to or less than a predetermined value is regarded as the in-apparatus load torque. The in-device load torque calculation means is configured to calculate the relationship of the in-device load torque with respect to the surface velocity from the in-device load torque and the surface speed by linear approximation. Further, in the invention described in claim 8, in the invention described in claim 6, the rotating body load torque when the speed difference between the surface speed and the belt speed is equal to or less than a predetermined value is regarded as the in-apparatus load torque. A load torque calculating means in the device for approximating the relationship between the surface torque and the load torque obtained by measuring the load torques for a plurality of surface velocities in the range where the speed difference is equal to or less than a predetermined value by curve approximation. Configured.

[0005]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. 1 is a system configuration diagram of a friction measuring system including a measurement target and a friction measuring device, showing a first embodiment of the present invention. As shown in the figure, the friction measuring system of this embodiment has a belt to be measured and a rotating body (rotating body for driving), and brings the belt into contact with the rotating body to drive the rotating body to drive the belt. A belt transport unit 1 for transporting, a rotary body driving torque generating unit 2 for generating torque in the rotary body to drive the rotary body to rotate, a rotary body surface speed measuring unit 3 for measuring the surface speed of the rotary body, and the speed of the belt. Based on the measured values of the rotating body surface speed, the belt speed and the rotating body load torque, and the rotating body load torque measuring section 5 for measuring the rotating body load torque generated in the rotating body. A frictional force calculation unit 6 that calculates a frictional force is provided. In addition, the belt transport unit 1
Is equipped with a belt tension generator 7 which is a belt tension generator that applies a load in the direction of gravity to the belt. An example of the belt tension generator 7 is shown in FIG. As illustrated, in the belt tension generator 7 of this example, the belt 11 is arranged so as to be wound around the rotating body 12 (driving rotating body). Then, the weight 13 for applying a desired tension to the belt 11
Is attached to the end portion of the belt 11, and the belt 11 is pressed against the rotating body 12 by the weight of the weight 13. Since the distance for driving and conveying the belt 11 for measuring the frictional force may be about 20 cm, such a configuration is possible.

FIG. 3 shows a specific example of the main part of the friction measuring system. In the example of FIG. 3, a motor 14 is used as the rotating body drive torque generating unit 2 that generates torque on the rotating body axis of the rotating body 12. Further, the belt speed measuring unit 4 irradiates the laser to two measurement positions on the surface of the rotating body, and measures the speed of the surface position by the phase difference (direction difference) of the radial variation of the two points. The belt position is detected by using the measuring device 15 or by previously providing linear patterns on the belt 11 at equal intervals in the direction perpendicular to the belt transport direction and detecting the linear patterns as the density using an optical sensor. A method of calculating the belt speed from the detected time is used. Further, as the rotating body surface speed measuring unit 3, the laser Doppler surface speed measuring device 15 is used.
(For example, another surface velocity measuring device 15
It is installed at a position avoiding the belt 11 for measurement), or an encoder 16 for detecting a rotation angle is attached to the rotary shaft, and the rotary position output from the encoder 16 is multiplied by the radius of the rotary body to obtain the surface of the rotary body. A method of converting the position to obtain the surface speed of the rotating body is used. Further, as the rotating body load torque measuring unit 5, a torque sensor 17 mounted between the motor 14 and the rotating body 12 is used. In addition, the motor 14
The clutch 18 is mounted between the rotor and the rotating body 12, and the motor 14
The torque generated in 1 is transmitted to the rotating body 12 or cut. A flywheel 19 is provided adjacent to the motor 14 on its rotation shaft to absorb uneven rotation. Further, in FIG. 3, the rotating body 12 to be measured is configured to be replaceable, and the rotating body 12 is replaced when measuring the frictional force of another rotating body. A computer including a keyboard and a mouse is used as the frictional force calculation unit 6. FIG. 4 shows an example different from the configuration shown in FIG. As shown, the basic configuration is the same as that shown in FIG. 3, but the clutch 18, the flywheel 1
In place of 9, the jack 20 is provided, and the mechanism around the shaft of the rotating body 12 is moved up and down by the jack 20. When the mechanism around the shaft is lowered, the weight 13 reaches the upper surface of the table, and The belt 11 floats from the rotating body 12.

FIG. 5 is an operation flow chart of the first embodiment. The operation of this embodiment will be described below with reference to FIG. In the configuration example shown in FIG. 3, first, the clutch 18 cuts the torque from the motor 14 to the rotating body 12. Next, torque is generated by the motor 14 (S
1) Rotate the flywheel 19 in advance. After that, the clutch 18 rapidly transmits the torque on the flywheel 19 side to the rotating body 12, thereby causing the belt 11 to slip relative to the rotation of the rotating body 12. Subsequently, the belt 11 gradually starts moving due to the frictional force generated between the belt 11 and the rotating body 12, and finally reaches the same speed as the surface of the rotating body. On the other hand, from the time when the belt 11 starts slipping until the speed becomes constant, the rotary body surface speed, the belt speed, and the rotary body load torque are respectively detected by the encoder 16, the laser Doppler surface speed measuring device 15, and the torque sensor 17. (S2). Then, the frictional force calculation unit 6 obtains the speed difference between the surface speed of the rotating body and the belt speed from these measured values, and calculates the frictional force from the relationship between the speed difference and the load torque of the rotating body (S3). The calculated example is shown in FIG. Further, in the example shown in FIG. 4, first, the rotating body 12 is sufficiently lowered by the jack 20 so that the frictional force is not transmitted to the belt 11. afterwards,
A torque is generated by the motor 14 (S1), and the rotating body 1
Rotate 2 in advance. However, in this state, the weight 13 reaches the table, and therefore the belt 11 floats from the rotating body 12, so that the belt 11 does not move. Next, the rotating body 12 is quickly pressed against the belt 11 by the jack 20, thereby causing the belt 11 to slip with respect to the rotation of the rotating body 12. Subsequently, the belt 11 gradually starts moving due to the frictional force generated between the belt 11 and the rotating body 12, and finally reaches the same speed as the surface of the rotating body.
On the other hand, the rotating body surface speed, the belt speed, and the rotating body load torque are measured by the encoder 16, the laser Doppler surface speed measuring device 15, and the torque sensor 17 from the time when the belt 11 starts to slip until the speed becomes constant. Yes (S2). Then, the frictional force calculation unit 6 calculates the speed difference between the surface speed of the rotating body and the belt speed from these measured values, and calculates the frictional force from the relationship between the speed difference and the load torque of the rotating body (S3). Thus, according to this embodiment, when measuring the frictional force between the rotating body and the belt, the belt is wound around the rotating body, a predetermined tension is applied to the belt, and the predetermined tension is applied between the rotating body and the belt. It is possible to generate a vertical reaction force and eliminate fluctuations in the vertical reaction force due to a shake in the belt thickness direction, and perform highly accurate friction force measurement.

Next, a second embodiment of the present invention will be described. FIG. 7 shows a block diagram of the configuration of this embodiment. As shown, the friction measuring system of this embodiment is shown in FIG.
In addition to the configuration of the first embodiment shown in FIG.
Is provided with a measurement control unit 21 capable of transmitting a recording start signal and a recording end signal. In this example,
The measurement control unit according to the second aspect is realized by the measurement control unit 21. FIG. 8 shows an operation flow of the second embodiment.
The operation of this embodiment will be described below with reference to FIG. In this embodiment, the motor 14 is processed in the same procedure as in the first embodiment.
Generates torque (S11), the torque sensor 17
Detects the rotor load torque, and the measurement control unit 21 recognizes the detection of the rotor load torque (S12). This allows
The measurement control unit 21 generates a recording start signal (S13), and the frictional force calculation unit 6 that has received the recording start signal causes the encoder 16, the laser Doppler surface speed measuring device 15, and the torque sensor 17 to rotate the rotor surface speed, respectively. , Belt speed, and rotating body load torque are measured (S1
4) The recording of the measurement result is started. On the other hand, after the recording start signal is generated, the measurement control unit 21 monitors the speed difference between the rotating body surface speed calculated by the frictional force calculation unit 6 and the belt speed (No in S15, S14), and the speed difference is detected in advance. If it becomes less than the stored predetermined value (Yes in S15)
s), a recording end signal is generated (S16). As a result, the frictional force calculation unit 6 recognizes the recording end signal, finishes the recording and the calculation of the speed difference (finishing the recording means ending the measurement of the surface speed of the rotating body), and the friction Force calculation is started (S17). Thus, according to this embodiment, the frictional force measurement can be ended when the speed difference between the surface speed of the rotating body and the belt speed falls within a predetermined range, so that the frictional force can be measured in a short time. it can. Even if the belt speed settles near the surface speed of the rotating body, the speed difference measured does not strictly become zero due to minute load fluctuations, minute torque fluctuations generated in the drive torque generator, measurement errors, etc. Therefore, it is possible to measure in a short time by stopping recording (measurement) when the speed difference becomes equal to or less than a predetermined value.

Further, in the friction measuring system according to the third embodiment of the present invention, as shown in FIG. 9, a belt end fixing portion which is a belt end fixing means for uniformly clamping the end portion of the belt 11 is provided. 23, a weight 13 that passes through the position of the center of gravity of the belt end fixing portion 23 and is loaded in the conveying direction of the belt 11.
Put on. As a result, in this embodiment, the belt tension distribution can be made uniform. The fourth aspect of the present invention
In the friction measuring system of the embodiment, as shown in FIG. 10, a cylindrical rotating body 24 (loading rotating body) is provided which is in contact with the inside of the ring-shaped belt 11a and rotates according to the movement of the belt 11a. The shaft of the rotating body 24 is not fixed, its axial direction is parallel to the rotating shaft of the rotating body 12, and the weights 13 are attached to both ends of the shaft of the rotating body 24, and the belt 11a is tensioned by its own weight. Generate. Thus, in this embodiment, since the belt 11a is ring-shaped, the belt is in constant contact with the rotating body,
Therefore, it is not necessary to determine the belt length in consideration of the time from the slip state until the belt speed settles near the surface speed of the rotating body, and the load can be applied uniformly over the width of the belt. The distribution of can be uniform.

Further, in the friction measuring system according to the fifth embodiment of the present invention, as shown in FIG. 11, inside the belt 11, in addition to the rotating body 12, the rotation can be changed in the vertical direction. A body 25 (contact angle changing rotary body) is provided, and the belt 11 is wound around the rotary body 25 when the weight 13 is mounted. As a result, in this embodiment, the wrapping angle of the rotator 12 can be changed by moving the rotator 25 different from the rotator 12 as the frictional force measurement target up and down, so that the desired wrapping angle can be obtained. Set,
The frictional force at the winding angle can be measured. In addition, in the example shown in FIG. 11, the winding angle is adjusted only by the rotating body 25, but one more rotating body is provided on the opposite side from the rotating body 12, and both the rotating body and the rotating body 25 are moved. By doing so, it is possible to set a small winding angle.

FIG. 12 is an operation flow chart showing the sixth embodiment of the present invention. In this embodiment, the frictional force calculation unit 6 that also operates as a frictional force correction unit corrects the error factor of the rotational body load torque measured by the rotational body load torque measuring unit 5 (see FIG. 1). Therefore, first, the frictional force calculation unit 6, which also operates as an in-apparatus load torque calculation unit, generates a friction torque between the belt 11 and the rotating body 12 other than the load torque generated by the rotation mechanism of this friction measuring system. The rotating body load torque (in-apparatus load torque such as viscous torque) is obtained as described later (S21). Alternatively, the in-device load torque such as the viscous torque obtained outside the friction measuring system is input using an in-device load torque input means such as a keyboard provided in the frictional force calculation unit 6. Then, from the rotating body load torque measured by the rotating body load torque measuring unit 5, the belt 11 and the rotating body 12 are
The load torque in the apparatus other than the load torque generated by the friction is subtracted between and, and the friction force is calculated based on this (S
22). As a result, according to this embodiment, when the in-apparatus load torque generated in the apparatus is not sufficiently small with respect to the frictional force, the influence of the in-apparatus load torque can be eliminated. The measurement accuracy can be improved. Next, a method of obtaining the in-apparatus load torque other than the frictional force between the belt and the rotating body such as the above-described viscous torque will be described. This method is based on the fact that when the load torque inside the device that does not depend on the speed is small, the viscous load torque that generates the load torque in proportion to the speed is the main factor of the load torque inside the device, and the belt speed When the body surface velocity is reached, the frictional force between the rotating body and the belt becomes small, and it is based on the fact that the viscous load torque is the main factor of the rotating body load torque. Therefore, in order to obtain such a torque, first, the rotating body load torque measuring unit 5 measures within a predetermined time in a state where the speed difference between the rotating body surface speed and the belt speed is equal to or less than a predetermined value. The rotating body load torque data is averaged to obtain an average load torque T1. Further, the surface speed data of the rotating body measured within the same predetermined time is averaged to obtain the average speed V1. Next, a linear expression that passes through the origin and the point (V1, T1) shown in FIG. 13 is obtained using the following calculation expression. T = T1 / V1 × V (Equation 1) Here, V is the surface speed of the rotating body, and T is the load torque of the rotating body (internal load torque) other than the frictional force between the belt and the rotating body. This is used as an in-apparatus load torque estimation formula, and the in-apparatus load torque T in Equation 1 corresponding to the surface speed of the rotating body is obtained using this estimation formula.

FIG. 14 is an explanatory diagram showing a seventh embodiment of the present invention. In the sixth embodiment, the relationship between the in-apparatus load torque and the surface speed of the rotating body is linearly approximated as shown by the equation 1, but in the seventh embodiment, it is approximated by a curve.
Therefore, first, in a state where the speed difference between the surface speed of the rotating body and the belt speed is equal to or less than a predetermined value, the load torque data of the rotating body measured within a predetermined time is averaged to obtain an average load torque T1 ( (See FIG. 14). Also, average the rotating body surface speed data measured within the same predetermined time,
The average speed V2 is calculated. Next, similarly, in the state where the speed difference is equal to or less than the predetermined value, the rotor surface speed is set to be near an arbitrary speed different from V1, and the rotor load torque T2 and the rotation speed are set in the same manner as described above. The body surface velocity V2 is measured.
Further, by repeating this in the range of the predetermined surface speed of the rotating body, the data of the load torque T with respect to the surface speed V of the rotating body is measured. Next, as shown in FIG. 14, a spline curve that smoothly connects the obtained points is obtained, and the following relational expression is calculated. T = F (V) (Equation 2) where V is the surface speed of the rotating body, T is the load torque of the rotating body other than the frictional force between the belt and the rotating body (internal load torque), and the function F is the spline curve formula. is there. This is referred to as the in-apparatus load torque estimation formula. Thus, according to this embodiment, it is possible to correct the frictional force with respect to the surface speed of the rotating body even if the load torque in the device has a nonlinear component.

[0013]

As described above, according to the present invention,
According to the first aspect of the invention, from the surface speed of the driving rotating body that drives the belt, the belt speed, and the rotating body load torque generated in the driving rotating body, the speed difference with respect to the speed difference between the surface speed and the belt speed is calculated. When measuring the frictional force generated between the drive rotating body and the belt, a load in the direction of gravity is applied to the belt, so a vertical reaction force is generated between the drive rotating body and the belt, which causes runout in the thickness direction. Fluctuation of the normal force due to is eliminated, so that the measurement accuracy of the frictional force can be improved. Further, the frictional force can be measured in a stretched state of the belt as in the case of operation. Also,
In the invention according to claim 2, in the invention according to claim 1, when the speed difference between the surface speed and the belt speed is equal to or less than a predetermined value set in advance, the measurement of the surface speed, the belt speed and the load torque of the rotating body. Since a recording end signal is generated to end the recording of the result, even if the belt speed settles near the surface speed of the rotating body, the speed difference measured is strictly due to minute load fluctuations, minute torque fluctuations, and measurement errors. It is possible to stop the measurement / recording even if does not become 0, so that the frictional force can be measured in a short time. According to a third aspect of the invention, in the first aspect of the invention, the end portions of the belt are uniformly fixed by the belt end fixing means, and the weight is attached to the position of the center of gravity of the belt end fixing means. Therefore, the tension distribution can be made uniform. According to a fourth aspect of the present invention, in the first aspect of the present invention, the belt is configured in a ring shape, and for a load that is inscribed in the belt and rotates below the drive rotating body together with the drive rotating body. A rotating body is provided, and tension is generated in the belt due to the weight of the load rotating body.Therefore, it is necessary to determine the belt length in consideration of the time from the slip state until the belt speed settles near the surface speed of the rotating body. And is evenly loaded across the width of the belt, thus providing a uniform tension distribution.

According to the invention described in claim 5, claim 1
In the invention described above, a contact angle changing rotary body that can move the position at least in the vertical direction is provided, and the contact angle of the belt with respect to the driving rotary body is changed by changing the position of the contact angle changing rotary body. Since it can be changed, a desired winding angle can be set and the frictional force in that state can be measured. According to a sixth aspect of the invention, in the first aspect of the invention, an in-apparatus load torque that is generated in addition to the frictional force between the driving rotating body and the belt is calculated or input, and the in-apparatus load torque is calculated. Since the frictional force is corrected by subtracting from the load torque,
When the in-apparatus load torque is not sufficiently small with respect to the frictional force, the influence of the in-apparatus load torque can be eliminated, and therefore, the measurement accuracy of the frictional force can be improved. Further, in the invention according to claim 7, in the invention according to claim 6, the rotating body load torque when the speed difference between the surface speed and the belt speed is equal to or less than a predetermined value is regarded as the in-apparatus load torque, Since the relation between the load torque in the device and the surface velocity is calculated by linearly approximating the load torque in the device to the surface velocity, the frictional force can be corrected. According to the invention of claim 8, claim 6
In the invention described, the rotating body load torque when the speed difference between the surface speed and the belt speed is equal to or less than a predetermined value is regarded as the in-apparatus load torque, and the speed difference is a plurality of surfaces within a predetermined value or less. Since the respective load torques with respect to the speed are measured, the relationship between the surface speed and the in-apparatus load torque can be approximated by a curve. Therefore, even if there is a non-linear component in the in-apparatus load torque, Correction is possible.

[Brief description of drawings]

FIG. 1 is a system configuration diagram of a friction measuring system showing a first embodiment of the present invention.

FIG. 2 is a perspective view of a main part of a friction measuring system showing a first embodiment of the present invention.

FIG. 3 is a perspective view of a friction measuring system showing a first embodiment of the present invention.

FIG. 4 is another perspective view of the friction measuring system showing the first embodiment of the present invention.

FIG. 5 is an operation flowchart of the friction measuring system showing the first embodiment of the present invention.

FIG. 6 is an explanatory diagram of a main part of the friction measurement system showing the first embodiment of the present invention.

FIG. 7 is a system configuration diagram of a friction measuring system showing a second embodiment of the present invention.

FIG. 8 is an operation flowchart of the friction measuring system showing the second embodiment of the present invention.

FIG. 9 is a perspective view of a main part of a friction measurement system showing a third embodiment of the present invention.

FIG. 10 is a perspective view of a main part of a friction measuring system showing a fourth embodiment of the present invention.

FIG. 11 is a perspective view of a main part of a friction measurement system showing a fifth embodiment of the present invention.

FIG. 12 is an operation flow chart of a friction measuring system showing a sixth embodiment of the present invention.

FIG. 13 is an explanatory diagram of a main part of a friction measuring system showing a sixth embodiment of the present invention.

FIG. 14 is an explanatory diagram of a main part of a friction measuring system showing a seventh embodiment of the present invention.

[Explanation of symbols]

1 Belt conveyor 2 Rotor driving torque generator 3 Rotating body surface speed measurement unit 4 Belt speed measurement unit 5 Rotor load torque measurement unit 6 Friction force calculator 7 Belt tension generator 11 belts 12 Drive rotor 13 weights 14 motor 15 Laser Doppler surface velocity measuring instrument 16 encoder 17 Torque sensor 18 clutch 19 flywheel 20 jacks 21 Measurement control unit 23 Belt end fixing part 24 rotator 25 rotating body

Claims (8)

[Claims] 1. The driving rotation with respect to the speed difference between the surface speed and the belt speed, based on the surface speed of the driving rotation body that drives the belt, the belt speed, and the rotating body load torque generated in the driving rotation body. A friction measuring device for measuring a frictional force generated between a body and a belt, comprising a belt tension generating means for applying a load in the direction of gravity to the belt. 2. The friction measuring device according to claim 1,
Measurement control means for generating a recording end signal for ending recording of the measurement results of the surface speed, the belt speed and the rotor load torque when the speed difference between the surface speed and the belt speed is equal to or less than a predetermined value set in advance. A friction measuring device comprising: 3. The friction measuring device according to claim 1,
The belt tension generating means includes belt end fixing means for uniformly fixing the end of the belt, and a weight is attached to a position of a center of gravity of the belt end fixing means. Measuring device. 4. The friction measuring device according to claim 1,
The belt is configured in a ring shape, and the belt tension generating means is provided below the drive rotating body with a load rotating body that rotates inscribed in the belt together with the drive rotating body.
A friction measuring device characterized in that tension is generated on the belt by the weight of the load rotating body. 5. The friction measuring device according to claim 1,
A configuration is provided in which a contact angle changing rotary body that can move the position at least in the vertical direction is provided, and the contact angle of the belt with respect to the driving rotary body is changed by changing the position of the contact angle changing rotary body. A friction measuring device characterized in that 6. The friction measuring device according to claim 1,
An in-apparatus load torque calculation means for calculating an in-apparatus load torque generated in addition to the frictional force between the driving rotating body and the belt, or an in-apparatus load torque input means for inputting an in-apparatus load torque value; A friction measuring device, comprising: a frictional force correction unit that corrects the frictional force by subtracting torque from the rotating body load torque. 7. The friction measuring device according to claim 6,
The in-apparatus load torque calculating means regards the rotating body load torque when the speed difference between the surface speed and the belt speed becomes a predetermined value or less as the in-apparatus load torque, and the in-apparatus load torque and the surface A friction measuring device characterized in that the relationship between the load torque in the device and the surface velocity is linearly approximated and calculated from the velocity. 8. The friction measuring device according to claim 6,
The in-apparatus load torque calculating means regards the rotating body load torque when the speed difference between the surface speed and the belt speed becomes a predetermined value or less as the in-apparatus load torque, and the speed difference is a predetermined value or less. A friction measuring device having a configuration in which a relationship between a load torque and a surface velocity obtained by measuring load torques for a plurality of surface velocities in a range is calculated by curve approximation.