JP2000298078A - Traction coefficient measuring device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an outer peripheral surface of a driving roller 9 and a driven roller 11.
The traction coefficient of the contact portion with the outer peripheral surface can be measured in a state according to the actual driving situation. An outer peripheral surface of a driving roller is brought into contact with an outer peripheral surface of a driven roller, and a pressing device applies a predetermined surface pressure to a contact portion. The driven shaft 16 supporting the driven roller 11 is freely displaceable about a vertical axis passing through the center of curvature of the generatrix of the outer peripheral surface of the driven roller 11. A traction force generated at the contact portion is measured by measuring a torque applied to the driving roller 9 by a driving torque measuring device 8 provided in the middle of the driving shaft 7.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The traction coefficient measuring apparatus according to the present invention uses a traction coefficient which has a great effect on the basic performance of a friction transmission (traction drive transmission) constituting a power transmission means of various mechanical devices. It is used for precise measurement under the condition according to the state.

[0002]

2. Description of the Related Art For example, use of a toroidal type continuously variable transmission, which is a kind of traction drive transmission, as a transmission for an automobile, a helicopter, and a ship has been studied. Alternatively, a traction drive transmission is used as a transmission for a spindle of a machine tool. In such a traction drive transmission, measuring a traction coefficient of a traction portion, which is a contact portion between members that transmit power by frictionally engaging with each other, is an important factor in designing a high-performance traction drive transmission. Important from.

[0003] For this reason, various traction coefficient measuring devices incorporating a pair of rollers for transmitting a rotational force by bringing their peripheral surfaces into contact with each other have been used. As described above, there are the following two types of methods for measuring the traction coefficient using a pair of rollers. The first method is that the driven roller is driven to rotate by the driving roller while a load is applied to the driven roller, and the slip ratio at the traction portion is determined from the rotational speeds of both the driving and driven rollers. At the same time, the traction force at the traction portion is determined from the torque applied to the driving roller. In the second method, a pair of rollers are driven to rotate at different rotational speeds (peripheral speeds), a predetermined slip ratio is forcibly applied to the traction portion, and a torque applied to the drive side roller is used to determine the traction portion. The traction power is required.

[0004]

SUMMARY OF THE INVENTION The present invention makes it possible to precisely measure the traction coefficient of a toroidal type continuously variable transmission used as a transmission for an automobile under conditions close to practical use. More specifically, the peripheral speed of the traction portion is 0 to 40 m / s, and the contact surface pressure _Pmax is 0 to 4
0GPa, traction oil temperature is -40 to +150
Under the condition of ° C., the above-mentioned traction coefficient can be measured while taking into consideration the spin generated under actual use conditions.

[0005]

A traction coefficient measuring apparatus according to the present invention comprises, similarly to a conventionally known traction coefficient measuring apparatus, a driving roller which is driven to rotate about a driving shaft by a driving source, and an outer periphery thereof. A driven roller that rotates with the driven shaft with the rotation of the driving roller by bringing the surface into contact with the outer peripheral surface of the driving roller; and a load device that applies resistance to the driven shaft to rotate the driven shaft. And

Particularly, in the traction coefficient measuring device of the present invention, the generatrix of the outer peripheral surface of at least one of the driving roller and the driven roller is a partial arc having the outer peripheral surface as a convex surface. The portion supporting the roller is freely displaceable relative to a vertical axis passing through the center of curvature of the generatrix.

[0007]

When the traction coefficient is measured by the traction coefficient measuring device of the present invention configured as described above,
The driving roller is driven to rotate, and the rotation of the driving roller is transmitted to the driven roller. The angle between the drive shaft and the driven shaft can be adjusted by relatively displacing the portion supporting both rollers, and the spin of the traction portion can be adjusted by adjusting the angle. Therefore, the traction coefficient can be precisely measured under conditions in accordance with a practical state.

[0008]

1 to 8 show a first embodiment of the present invention. As shown in FIG. 6, the traction coefficient measuring device of the present invention adjusts a fluid pressure for applying a predetermined surface pressure to a traction transmission unit and a test machine main body 1 for performing traction transmission under predetermined conditions. A fluid pressure adjusting device 2, a sample oil supply device 3 for supplying sample oil such as traction oil whose temperature has been adjusted to the traction transmission portion, and a load device for applying resistance to the traction portion. Cooling device 4 and the tester main body 1
And a measurement processing device 5 for measuring each state in the portion and further processing the measured data. As shown in FIG. 7, the measurement processing device 5 includes an oil temperature sensor 6 for measuring the temperature of the sample oil supplied by the sample oil supply device 3 and a drive-side roller 9 described later. Driven roller 11
(See FIGS. 1 and 2) A load measuring device 15 for measuring the load applied to the drive shaft 7 (see FIGS. 1 and 2)
A drive-side torque measuring device 8 for measuring the torque transmitted through the drive shaft, a drive-side rotation detector 10 for detecting the rotational speed of the drive-side roller 9 that is rotationally driven by the drive shaft 7, and Rotates with the rotation of the roller 9,
A driven-side rotation detector 12 for detecting the rotation speed of the driven-side roller 11, and a driven-side torque measuring device 13 for measuring a torque applied to a driven shaft 16 (FIG. 1) that rotates together with the driven-side roller 11. And

As shown in FIG. 7, the measurement data of each of these detection elements is input to an arithmetic processor 14 such as a microcomputer. Then, the arithmetic processing unit 14 calculates a traction coefficient μ from the detected value F of the load measuring device 15 and the detected value Tq _{1 of the} driving torque measuring device 8.
Further, the arithmetic processing unit 14 calculates the outer peripheral surface of the driving roller 9 and the driven roller, which are traction units, from the measured values N ₁ and N _{2 of the} driving side and driven side rotation detectors 10 and 12. The slip ratio s of the contact portion with the outer peripheral surface of No. 11 is calculated.
The arithmetic processing unit 14 detects the detected values Tq ₁ , Tq _{2 of the} drive-side and driven-side torque measuring devices 8, 12 and the measured value N _{1 of the} drive-side, driven-side rotation detectors 10, 12. , N ₂
From this, the efficiency of power transmission at the contact portion between the outer peripheral surface of the driving-side roller 9 and the outer peripheral surface of the driven-side roller 11 Ｎ = (N
₂ · Tq ₂ ) / (N ₁ · Tq ₁ )｝ is calculated. The arithmetic processor 14 sends the calculated value of the traction coefficient μ and the calculated value of the slip ratio s to the plotter 17, and causes the plotter 17 to output a measured value as shown in FIG. 8, for example. Further, the arithmetic processing unit 14 compares the slip ratio s with a set value, and when the slip ratio exceeds the set value,
The tester main body 1 is stopped by the safety device 18.

A support plate 21 for the drive unit and a support plate 22 for the driven unit are provided on the upper surface of the platen 20 constituting the upper surface of the frame 19 constituting the tester main body 1 described above. Of these, the drive unit support plate 21 is perpendicular to the direction in which the drive shaft 7 is disposed (the left-right direction in FIG. 1) with respect to the surface plate 20 by the linear motion bearings 23, 23. (The vertical direction in FIG. 1). On the other hand, the driven unit supporting plate 22 is provided on the surface plate 20 by a pivot 44 (FIGS. 3 and 4) so that the mounting angle can be adjusted. The center axis O of this angle adjustment is a vertical axis passing through the center of curvature of the generatrix of the outer peripheral surface of the driven roller 11 (described below, which is close to the driving roller 9 among the arcs obtained by connecting points that are the centers of curvature). (The axis that coincides with the tangent drawn vertically in the part).

A drive shaft 7 is rotatably supported on the upper surface of the drive unit support plate 21. This drive shaft 7
Arranges the base end portion 7a and the front end portion 7b concentrically with each other,
The drive side torque measuring device 8 is connected between the two end portions 7a and 7b in series by couplings 24a and 24b. The base end 7a is rotatably supported by a pair of rolling bearing units 25 on the upper surface of the drive unit support plate 21. On the other hand, the tip end portion 7b is rotatably supported by a rolling bearing on a drive-side roller support bracket 26 fixed to the upper surface of the drive-side unit support plate 21 and having a U-shaped planar shape. I have. In this rolling bearing, at least one pair of angular type ball bearings is used in a back-to-back or front-to-back combination in order to have low rolling resistance and to be able to support not only a radial load but also a thrust load generated by spin. The drive-side roller 9 is fixed to the front end portion 7b at an inner portion of the drive-side roller support bracket 26. In addition, the drive-side roller support bracket 2
The rotation speed (rotation amount) of the distal end portion 7b can be detected by a drive-side rotation detector 10, such as a rotary encoder, provided on the outer surface of the motor 6. On the other hand, a driven pulley 27 is fixed to the end of the base end 7a, and an endless belt 29 is fixed between the driven pulley 27 and a driving pulley 28 fixed to a rotating shaft of a motor 43 as a driving source. Over,
The drive shaft 7 is freely rotatable.

The central axis of the driving roller 9 coincides with the central axis of the driving shaft 7. The generatrix of the outer peripheral surface of the driving roller 9 is a straight line parallel to the rotation center of the roller. Therefore, the outer peripheral surface of the driving roller 9 is
It is a cylindrical surface whose center is the center axis of the drive shaft 7.
The driving unit supporting plate 21 supporting the driving roller 9 on the upper surface thereof is, as described above, the platen 2.
The upper surface of the drive shaft 7 is supported by the linear motion bearings 23, 23 so as to be horizontally movable in a direction perpendicular to the direction in which the drive shaft 7 is disposed. Further, a pressing device 30 such as an air cylinder is provided between the upper surface of the surface plate 20 and the driving-side roller support bracket 26, and the driving-side roller support bracket 26 is attached to the driven-side roller 11. And can be freely pressed. That is, the air cylinder serving as the pressing device 30 can freely put the piston rod 31 in and out by supplying and discharging compressed air. When the piston rod 31 projects, the drive-side roller support bracket 26 is
It is pressed through a load measuring device 15 such as a load cell, so that the contact pressure between the outer peripheral surface of the driving roller 9 and the outer peripheral surface of the driven roller 11 can be increased.

On the other hand, the driven roller 11 is rotatably supported by a driven roller support bracket 32 fixed to one corner (the lower left corner in FIG. 1) of the upper surface of the support plate 22 for the driven unit. . The driven shaft 16 is rotatably supported on the upper surface of the driven unit supporting plate 22. The driven shaft 16 has a base end portion 16a and a distal end portion 16b concentrically arranged, and a driven torque measuring device 13 between the both end portions 16a and 16b is connected to a coupling 33.
a and 33b connected in series. The base end 16
“a” is rotatably supported on the upper surface of the driven-side unit support plate 22 by a pair of rolling bearing units 34, 34. On the other hand, the front end 16b is fixed to the upper surface of the support plate 22 for the driven unit, and the support bracket 32 for the driven roller having a U-shape in plan view.
In addition, it is rotatably supported by rolling bearings. This rolling bearing also uses at least one pair of angular type ball bearings in a back combination or a front combination. The driven-side roller 11 is fixed to the tip 16b at an inner portion of the driven-roller support bracket 32. The rotation speed (rotation amount) of the tip 16b is determined by a driven rotation detector 12, such as a rotary encoder, provided on the outer surface of the driven roller support bracket 32.
Can be detected freely.

The other side of the upper surface of the driven unit support plate 22 (upper right corner in FIG. 1) is provided with the driven roller 1
Load shaft 35 for providing resistance against rotation of 1
Are rotatably supported by the rolling bearing units 34a, 34a. The proximal end of the load shaft 35 is connected to a load device 36 such as an electromagnetic brake, which serves as a resistance to the rotation of the load shaft 35. During operation of the traction coefficient measuring device, the load device 36 is cooled by the cooling device 4. Further, an endless belt 39 is stretched between a pulley 37 fixed to the distal end of the load shaft 35 and a pulley 38 fixed to the end of the base end 16a of the driven shaft 16,
The resistance caused by the load device 36 is changed by the driven roller 11.
It can be freely added to.

In the case of this embodiment, the generatrix of the outer peripheral surface of the driven roller 11 is a partial arc having the outer peripheral surface as a convex surface.
As described above, the support plate 22 for the driven unit supporting the driven roller 11 is connected to the platen 20 by the pivot 44, as shown in FIGS. The mounting angle position can be adjusted around the center axis O, which is a vertical axis passing through the center of curvature of the generatrix of the outer peripheral surface of the roller 11. The drive unit support plate 21
Can move only in parallel with respect to the surface plate 20. Therefore, the driven unit support plate 22 is relatively displaceable relative to the drive unit support plate 21 about the central axis O. For this reason, in the case of the present example, each of the pivot shafts 4 is provided on the support plate 22 for the driven unit.
A plurality of arc-shaped long holes 40, 40 are formed around the central axis O, which is also the center of 4. Then, bolts 41, 41 inserted through these elongated holes 40, 40 from above.
Are screwed into screw holes formed in the surface plate 20. When adjusting the position of the driven unit support plate 22, the bolts 41 are loosened to displace the driven unit support plate 22 about the central axis O. On the other hand, when the supporting plate 22 for the driven unit is fixed to perform the measuring operation, the bolts 41 are tightened.

Further, an oil supply nozzle 42 is provided above the driving roller 9 and the driven roller 11, and a temperature controlled traction oil or the like is applied to a contact portion between the outer peripheral surfaces of the rollers 9 and 11. Sample oil can be supplied freely. That is, by the sample oil supply device 3, -40 to +1
A sample oil such as traction oil adjusted to a predetermined temperature selected within a range of 50 ° C. is poured into a contact portion between the outer peripheral surfaces of the rollers 9 and 11. The temperature of the sample oil such as traction oil poured into the abutting portion depends on the oil supply nozzle 42.
Is measured by the oil temperature sensor 6 provided at the front end of the oil temperature sensor.

When the traction coefficient is measured by the traction coefficient measuring apparatus of the present embodiment configured as described above, first, a predetermined spin is generated at a contact portion between the outer peripheral surfaces of the rollers 9 and 11. Thus, the mounting position of the driven-side unit support plate 22 with respect to the surface plate 20 is adjusted. The degree of the spin is smaller as the driven shaft 16 supported on the upper surface of the driven unit support plate 22 and the drive shaft 7 are closer to being parallel to each other, and is larger as the angle between the shafts 16 and 7 is larger. Become. In this way, in order to change the degree of spin, the bolts 41, 41 are inserted into the slots 40, 4
0, the supporting plate 22 for the driven unit
Even if the mounting position is adjusted, the contact state between the outer peripheral surfaces of the rollers 9 and 11 does not become uneven. After the mounting position of the support plate 22 for the driven unit is adjusted in this manner, the sample oil adjusted to a predetermined temperature is supplied from the oil supply nozzle 42 to the contact portion between the outer peripheral surfaces of the rollers 9 and 11. Pour into.

Next, the driving-side roller support bracket 26 is moved by the pressing device 30 to the driven-side roller 1.
Press towards 1. As a result, the driven side roller 11
At the contact portion between the outer peripheral surface of the driving roller 9 and the outer peripheral surface of
A predetermined contact surface pressure _Pmax acts. This contact surface pressure _Pmax
Is adjusted in the range of 0 to 4 GPa. This contact surface pressure _Pmax
Is adjustable by the pressing force of the pressing device 30 and the contact area between the peripheral surfaces of the rollers 9 and 11. When the pressing device 30 is an air cylinder, the pressing force can be arbitrarily adjusted by changing the pressure of the compressed air sent into the cylinder by the fluid pressure adjusting device 2. The contact area can be adjusted by changing the outer diameters of the rollers 9 and 11 and the radius of curvature of the generatrix of each outer peripheral surface in addition to the pressing force.

Next, the drive roller 9 is rotated by the motor 43 via the drive pulley 28, the endless belt 29, the driven pulley 27, and the drive shaft 7. The rotation speed of the drive roller 9 can be adjusted in the range of 0 to 40 m / s in peripheral speed by changing the rotation speed of the motor 43. When performing a measurement operation, the rotational speed is maintained after accelerating to a desired rotational speed. When the driving roller 9 is rotationally driven in this manner, the torque applied to the driving roller 9 by the driving torque measuring device 8 provided between the base end portion 7a and the distal end portion 7b of the driving shaft 7. Is measured.

After the preparatory work described above, a load is gradually applied to the driven roller 11 by the load device 36, which had no load, until the driven roller 11 rotates. Then, the measurement values of the load measuring device 15, the driving-side torque measuring device 8, and the driving-side rotation detector 10 are processed by the arithmetic processing unit 14, and the plotter 17 shown in FIG. As shown, a curve representing the relationship between the slip ratio s and the traction coefficient μ is obtained for each spin value. In the measuring operation for obtaining such a curve, the load by the load device 36 is increased, the driven roller 11 does not rotate, and only the driving roller 9 rotates. Can be done in real time. Further, when a gross slip occurs, the safety device 18 sets the motor 4
3 is stopped, and the operation of the tester main body 1 is prevented from continuing in this gross slip state, thereby preventing damage to each component of the tester main body 1.

The value of the spin can be adjusted by displacing the driven shaft 16 to which the driven roller 11 is fixed around the center axis O. Therefore, the traction coefficient can be precisely measured under conditions in accordance with a practical state. The torque detected by the drive-side torque measuring device 8 includes, besides the traction force generated at the contact portion between the outer peripheral surfaces of the drive-side and driven-side rollers 9 and 11, the drive shaft 7 supports the drive-side roller. The dynamic torque of the rolling bearing supported by the bracket 26 and the dynamic torque of the rolling bearing supporting the driven shaft 16 by the driven roller support bracket 32 are included. In order to obtain an accurate traction force by eliminating the dynamic torque of each of the rolling bearings, before measuring the traction coefficient under a predetermined test condition, each time the rolling bearing under the test condition is used. It is necessary to measure the dynamic torque of the motor. In addition, the verification of the dynamic torque of the rolling bearing provided in the driving side torque measuring device 8 is performed separately by the method specified for the driving side torque measuring device 8.

The dynamic torque of each of the rolling bearings is measured by measuring the surface pressure of the contact portion between the outer peripheral surfaces of the rollers 9 and 11 (the pressing force by the pressing device 30), the peripheral speed of the outer peripheral surface of the driving roller 9, The type and temperature of the sample oil and the spin of the contact portion are set to the predetermined test conditions, and the test is performed without applying a load to the driven roller 11. In this state, the slip ratio s between the outer peripheral surfaces of the rollers 9 and 11 is 0.01%.
Or less. Therefore, the torque value detected by the drive-side torque measuring device 8 under such operating conditions is
The dynamic torque of each of the above rolling bearings is used.

This operation is more specifically performed as follows. First, the coupling 33b provided between the distal end portion 16b of the driven shaft 16 and the driven torque measuring device 13 is removed, and the driven torque measuring device 13 and the rolling bearing units 34, 34 To avoid resistance to rotation of Also, the mounting angle position of the driven unit support plate 22 is adjusted so that the spin value of the contact portion becomes a predetermined value. Then, sample oil adjusted to a predetermined temperature is supplied from the oil supply nozzle 42 to the contact portion. Next, the driving-side roller support bracket 26 is pressed against the driven-side roller 11 by the pressing device 30 so that the surface pressure of the contact portion becomes a desired value. Next, the drive roller 9 is driven by the motor 43 and accelerated to a predetermined number of revolutions, and then the number of revolutions is maintained. In this state, the operation is performed until the torque measured by the driving-side torque measuring device 8 is stabilized, and the measured value of the driving-side torque measuring device 8 is recorded to be the dynamic torque of each rolling bearing. The dynamic torque of each rolling bearing obtained in this way is subtracted (subtracted) from the torque obtained during the operation of measuring the traction coefficient, and based on the value of the resulting torque, the drive side, The traction force generated at the contact portion between the outer peripheral surfaces of both the passive rollers 9 and 11 is calculated.

Next, FIGS. 9 to 15 show a second example of the embodiment of the present invention. In the case of this example, the outer peripheral surface of the driven-side roller 11 is a partial spherical surface whose center point is the radius of curvature of the driven-side roller 11. In other words, the outer peripheral surface of the driven roller 11 exists on the same spherical surface whose center is the curvature of the driven roller 11. The center axis O, which is the center of the pivot 44 for supporting the driven-side unit support plate 22 so that the mounting angle position can be adjusted with respect to the surface plate 20, is defined as a vertical axis passing through the center point of the driven roller 11. I have.

In the case of this embodiment having such a configuration, even when the outer diameter of the driven roller 11 is changed, the driven roller 1
When changing the spin of the contact portion between the outer peripheral surface of the drive roller 9 and the outer peripheral surface of the drive roller 9, the driven unit support plate 22 may be displaced about the same pivot 44 with respect to the surface plate 20. it can. FIG. 9 shows a driven roller 11 having a relatively small diameter.
Is used to measure the traction coefficient. 10 to 11 show a state in which the drive shaft 7 and the driven shaft 16 are made parallel to each other by using a relatively small-diameter driven-side roller 11 so as to reduce the spin to zero, and FIG. In order to make the driven shaft 16 inclined with respect to the drive shaft 7, respectively, the respective states are shown. On the other hand, FIG. 13 shows a state in which the traction coefficient is measured using the driven roller 11a having a relatively large diameter. FIG. 14 shows that the driven shaft 7 and the driven shaft 16 are driven by using the driven roller 11a having a relatively large diameter so as to reduce the spin to zero.
And FIG. 15 shows a state where the driven shaft 16 is inclined to be larger than the drive shaft 7 in order to increase the spin.

As is apparent from a comparison between FIG. 9 and FIG. 13, even if the diameter of the driven rollers 11 and 11a is changed,
Only by the parallel movement of the drive unit support plate 21 by the linear motion bearing 23, the difference in the outer diameter of the driven rollers 11, 11a is absorbed. As is apparent from a comparison between FIGS. 10 to 12 and FIGS. 14 to 15, the driven rollers 11, 11a
Regardless of the outer diameter difference, the spin can be changed by displacing the driven unit support plate 22 about the same pivot 44. In the illustrated example, the driven roller 1
Even when the outer diameters of 1, 11a are changed, the outer diameter of the driving roller 9 is not changed, but can be changed freely.

In each of the illustrated examples, the generatrix on the outer peripheral surface of the driving roller 9 is a straight line, and the generatrix on the outer peripheral surface of the driven rollers 11 and 11a is a circular arc. . Further, the generating lines on the outer peripheral surfaces of both the driving side and driven side rollers 9, 11, 11a may be arcs. Furthermore,
Instead of the supporting plate 22 for the driven unit, the supporting plate for displacing the vertical pivot 44 to change the spin value may be the supporting plate 21 for the driving unit. However, in this case, the driven unit support plate 22 is supported by the linear motion bearing, and the driven roller support bracket 26 is freely pressed by the pressing device 30.

[0028]

The traction coefficient measuring apparatus of the present invention
With the configuration and operation described above, the traction coefficient can be accurately and accurately measured under the conditions in accordance with the actual driving situation, and can contribute to the improvement of the performance of various friction transmission devices such as a friction transmission.

[Brief description of the drawings]

FIG. 1 is a plan view showing a first example of an embodiment of the present invention.

FIG. 2 is a front view of a part of FIG.

FIG. 3 is an enlarged sectional view taken along the line AA of FIG. 1 and a partial plan view, partially omitted.

FIG. 4 is a view in which a part is omitted and viewed from the left side of FIG. 3;

FIG. 5 is a partial plan view showing a relationship between a driven roller and a long hole.

FIG. 6 is a block diagram showing the overall configuration.

FIG. 7 is a block diagram of a measurement processing device.

FIG. 8 is a graph showing an example of a measurement result.

9A and 9B show a second example of the embodiment of the present invention in a state where a small-diameter driven-side roller is used, and a part thereof is omitted.
The figure corresponding to the arrow view.

FIG. 10 is a front view of a part of FIG.

FIG. 11 is a bottom view of the same seen from below in FIG. 9;

FIG. 12 is a view similar to FIG. 10, showing a state where spins are generated;

FIG. 13 is a view similar to FIG. 9, showing a state where a large-diameter driven-side roller is used and a part of which is omitted.

FIG. 14 is a front view of a partly omitted view seen from above in FIG. 13;

FIG. 15 is a view similar to FIG. 14, showing a state where spins are generated;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Test machine main body 2 Fluid pressure adjusting device 3 Sample oil supply device 4 Cooling device 5 Measurement processing device 6 Oil temperature sensor 7 Drive shaft 7a Base end 7b Tip 8 Drive-side torque measuring device 9 Drive-side roller 10 Drive-side rotation detection Apparatus 11, 11a Driven roller 12 Driven rotation detector 13 Driven torque measuring instrument 14 Processing unit 15 Load measuring instrument 16 Driven shaft 16a Base end 16b Tip 17 Plotter 18 Safety device 19 Frame 20 Surface plate 21 Drive side Unit support plate 22 Drive side unit support plate 23 Linear motion bearing 24a, 24b Coupling 25 Rolling bearing unit 26 Drive side roller support bracket 27 Drive pulley 28 Drive pulley 29 Endless belt 30 Pressing device 31 Piston rod 32 Drive side roller Support brackets 33a, 33b couplings 34, 3 a rolling bearing unit 35 load shaft 36 load device 37 pulley 38 pulley 39 endless belt 40 elongated hole 41 a bolt 42 the fueling nozzle 43 motor 44 pivot

 ────────────────────────────────────────────────── ─── Continuing from the front page (72) Inventor Shinichi Natsume 1-50 50 Kugenuma Shinmei, Fujisawa-shi, Kanagawa F-term in NSK Ltd. (reference) 2F051 AA01 AB02 AB06 AC01 AC09 BA03 2G024 AB20 BA11 CA11 DA02

Claims (5)

[Claims] A drive roller, which is driven to rotate about a drive shaft by a drive source, and an outer peripheral surface of which is brought into contact with an outer peripheral surface of the drive roller to rotate together with the driven shaft with the rotation of the drive roller. In a traction coefficient measurement device including a driven roller and a load device that applies a resistance to rotation of the driven shaft to the driven shaft, at least one of the driving roller and the driven roller The bus of the outer peripheral surface is a partial arc having the outer peripheral surface as a convex surface, and the portion supporting the roller is capable of relative displacement about a vertical axis passing through the center of curvature of the bus. Coefficient measuring device. 2. A bus of the outer peripheral surface of one of the driving roller and the driven roller is a partial arc having the outer peripheral surface as a convex surface, and a generating line of the outer peripheral surface of the other roller is the other of the other rollers. The traction coefficient measurement device according to claim 1, wherein the traction coefficient measurement device is a straight line parallel to a rotation center of the roller. 3. The outer peripheral surface of one roller is a partial spherical surface having the center point of the one roller as the center of the radius of curvature, and the vertical axis passing through the center of curvature of the outer peripheral surface of the one roller is The traction coefficient measurement device according to claim 1, wherein the traction coefficient measurement device passes through a center point of the roller. 4. The traction coefficient measuring device according to claim 1, wherein a torque detector is provided between the driving source and the driving roller and between the load device and the driven roller. 5. The traction coefficient measuring device according to claim 1, wherein traction oil whose temperature is controlled is freely sprayed to a contact portion between an outer peripheral surface of the driving roller and an outer peripheral surface of the driven roller.