JPH09159000A - Toothed belt driving gear and toothed belt - Google Patents

Abstract

PROBLEM TO BE SOLVED: To set speed regulation as small as possible, improve printing accuracy or conveying accuracy, also reduce starting torque even at an ordinary and low temperature as a belt with a low shaft load required, and decrease a shaft load applied to a motor shaft, in a toothed belt driving gear. SOLUTION: In a toothed belt driving gear, a single pitch difference between a single pitch 4 of a belt tooth part 2 of a toothed belt 1 and a single pitch 8 of a pulley groove part 6 of a pulley 5 is limited to -0.04 to 0mm, a height of the belt tooth part is formed equal to or larger than a depth of the pulley groove part, and this height/depth ratio is set to 1.00 to 1.20. As a core wire of the toothed belt 1, an aramid fiber rope of 0.10 to 0.20mm diameter, obtained by single-twist bundling at least one or more filament groups converging an aramid fiber consisting of monofilament of 0.5 to 2.0 denier, is used.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toothed belt driving device and a toothed belt, and more particularly to a conveyor belt driving device and a conveyor belt driving device for use in a printer carriage belt, a banknote conveying belt, a card conveying belt and the like. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a belt, and more particularly to a flexible toothed belt drive device and a toothed belt that require positioning accuracy and low axial load, and have low rigidity even at low temperatures.

[0002]

2. Description of the Related Art Conventional carriage belts for printers,
Toothed belts used as banknote transfer belts and card transfer belts do not have a single-pitch tolerance for belt teeth or a single-pitch tolerance for pulley teeth. For example, the tolerance is set by measuring the pitch circumference or the axial distance, and the outer diameter tolerance is set for a pulley. And, as the core wire of the belt, aramid fiber rope or glass fiber rope is used,
The aramid fiber rope is disclosed in, for example, JP-A-54-13595.
As disclosed in Japanese Patent Publication No. 4, the twist coefficient is 1.4 to
2.6, with a thickness of 300-500 denier. Another aramid fiber rope has been developed in which a plurality of original yarns are aligned, twisted, and then subjected to an adhesive treatment. On the other hand, the glass fiber rope is also subjected to an adhesive treatment.

[0003]

However, the toothed belt used as the conventional carriage belt for printers, bill conveying belt, and card conveying belt as described above has a single pitch of belt teeth and a pulley groove. Since the pitch difference with the single pitch of is not limited, if the single pitch difference between the belt teeth and the pulley teeth is large, interference during engagement is likely to occur, which causes vibration of the belt,
There was a defect that the belt speed fluctuates, which adversely affects printing accuracy or conveyance accuracy.

Moreover, in the case of the conventional belt, the pulley groove is formed relatively deep with the belt tooth height and the pulley groove depth being substantially the same, so that the rotation center line of the belt also meshes with the belt tooth and the pulley groove. When the teeth of the belt 1 are engaged with the grooves of the pulley 5 and wound around as shown by the arrow in FIG. 12, the belt 1 takes on a slightly foldable shape and becomes polygonal due to the interference. There was also a drawback that increased the volatility.

The conventional toothed belt using aramid fiber or glass fiber as described above is suitable when a high modulus is required. For example, a belt for a small motor, a carriage belt for a printer, a banknote. Flexibility is lacking when a low axial load is required for the transfer belt, card transfer belt, etc. Also, the starting torque does not decrease because the rigidity is high even when used at low temperatures, and the axial load applied to the shaft There was a problem that it did not decrease.

The present invention solves such a problem, in particular, by considering the difference in the single pitch between the belt tooth and the pulley groove, and also considering the relationship between the belt tooth height and the pulley groove depth. By this, the carriage belt for the printer,
For toothed belt drive devices and toothed belts used for banknote transportation belts, card transportation belts, etc., speed fluctuations are suppressed as much as possible to improve printing accuracy or transportation accuracy, and the starting torque is supple even at low temperatures. It is an object of the present invention to provide a toothed belt drive device and a toothed belt that can reduce the axial load on the motor shaft.

[0007]

That is, a feature of the present invention which meets the above-mentioned object is to provide a toothed belt drive apparatus which winds a toothed belt between at least a pair of toothed pulleys to perform a reciprocating motion or a one-way motion. In the toothed belt drive device, the difference in the single pitch between the belt teeth and the pulley groove is set in the range of -0.04 to 0 mm to minimize the speed fluctuation rate of the belt.

Here, in the present invention, the ratio of the belt tooth height to the pulley groove depth is expressed as belt tooth height / pulley groove depth =
1.00 to 1.20 is preferable, and a toothed belt drive device in which the shape of the belt teeth and the pulley groove is trapezoidal is also included, and the belt of the toothed belt used in the above toothed belt drive device. The core wire embedded in the body is
A diameter of 0.10 to 0.20 obtained by bundling at least one filament group in which aramid fibers made of monofilament having a denier of 0.5 to 2.0 are bundled and twisted.
It also includes a toothed belt drive that is a mm aramid fiber rope.

Further, according to the present invention, the pitch between the core wires embedded in the belt main body of the toothed belt to be used is 0.2 to.
The toothed belt driving device having a range of 0.5 mm and the toothed belt driving device in which the tooth cloth is treated only with the resorcin-formalin-latex liquid and the rubber of the tooth portion is not exposed from the opening of the canvas are also characteristic. Finally, by combining the above respective configurations, the difference between the single pitch between the belt tooth and the pulley groove is set to −0 by setting the belt tooth height / pulley groove depth = 1.00 to 1.20. It was obtained by bundling at least one or more filament groups in which aramid fibers made of monofilaments having a core of the belt main body of 0.5 to 2.0 denier are bundled and set in a range of 0.02 to 0 mm. An aramid fiber rope having a diameter of 0.10 to 0.20 mm, a pitch between core wires of 0.2 to 0.5 mm, and a tooth cloth covered with the surface of the tooth portion of the belt to form a resorcin-
It is also characterized by a toothed belt drive device having a belt which is treated only with a formalin-latex liquid and which prevents the rubber of the tooth portion from being exposed from the opening of the canvas.

Further, according to the present invention, as set forth in claim 8, the present invention is obtained by bundling at least one aramid fiber composed of monofilaments having a core diameter of 0.5 to 2.0 denier and bundling at least one of them. Diameters 0.10-0.
A 20 mm aramid fiber rope having a pitch between core wires of 0.2 to 0.5 mm, and the tooth cloth coated on the surface of the tooth portion of the belt is treated only with the resorcin-formalin-latex liquid, and the rubber of the tooth portion is rubber. Another feature of the toothed belt is that the belt is not exposed through the opening of the canvas.

[0011]

According to the present invention, in the toothed belt drive device, by limiting the range of the pitch difference between the belt tooth single pitch and the pulley groove single pitch, the engagement between the belt teeth and the pulley groove can be improved. The smooth meshing reduces the interference between the belt teeth and the pulley groove, which suppresses the fluctuation of the belt speed, thereby further improving the printing accuracy and the transportation accuracy. Belt height / pulley groove depth =
When it is wound around a pulley by setting it to 1.00 to 1.20, the gap between the belt tooth groove and the pulley tooth tip becomes large, and the position of the center line of rotation of the belt on the pulley rises, resulting in a polygonal shape. Is reduced and the position of the center line of rotation does not fluctuate much up and down, thus reducing the speed fluctuation rate. Also, the core of the toothed belt is 0.10 to 0.20 m
By using a thin aramid fiber rope made of m, the belt itself is soft and supple even at room temperature and low temperature atmosphere, and the linear expansion coefficient of aramid fiber is negative, so at low temperature of -35 to 5 ° C. It is possible to reduce the tension on the shaft, reduce the starting torque, reduce the load on the shaft, and reduce the electric capacity of the small motor.

Further, since the tooth cloth is treated only with the RFL liquid, the opening of the tooth cloth is small, and it is difficult for the tooth cloth to expand, so that the rubber of the tooth portion is not exposed from the surface and the scattering of the rubber powder can be prevented. Further, the solid content of the resin adhering to the tooth surface reduces the friction coefficient of the surface and reduces the noise when the belt is driven.

[0013]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1A is a part of the toothed belt 1 of the toothed belt drive device of the present invention, and FIG.
(B) has shown a part of toothed pulley 5 engaged with it. At this time, the single pitch 4 of the belt tooth portion 2 in the figure
And the difference of the single pitch 8 of the pulley groove portion 6 is −0.04 to
It is set in the range of 0 mm, preferably in the range of -0.02 to 0 mm. Here, the single pitch difference between the belt and the pulley is expressed by the following equation (1). (1) Single pitch difference = {(belt single pitch)-(pulley single pitch)} However, belt single pitch = {(distance between shafts) / (number of belt teeth-measurement pulley teeth)} × 2 Pulley single pitch = {(pulley outer diameter + 2 x PLD) x
π} / number of pulley teeth. PLD = 0.254 mm and the number of pulley teeth was 10. As shown in FIG. 3, when the single pitch difference between the belt and the pulley is less than −0.04 mm, the speed fluctuation rate increases sharply, which causes the printing accuracy or the conveyance accuracy to deteriorate drastically. Even if the single pitch difference exceeds 0 mm, the rate of speed fluctuation sharply increases, and the printing accuracy or conveyance accuracy sharply deteriorates. The speed fluctuation rate becomes the minimum when the single pitch difference between the belt and the pulley is within the range of -0.02 to 0 mm, and within this range, the printing accuracy or the transportation accuracy is most stable.

Further, the relationship between the belt tooth height and the pulley groove depth also plays an important role in the speed fluctuation rate, and it is possible to set belt tooth height / pulley groove depth = 1.00 to 1.20. It is effective. When it is wound around the pulley by making the pulley groove depth shallower than before, the gap between the belt tooth groove and the pulley tooth tip becomes large, and the position of the center line of rotation of the belt on the pulley rises, Polygonization is eased,
The position of the center line of rotation does not fluctuate much up and down, and therefore the speed fluctuation rate becomes small. On the other hand, when the belt tooth height / pulley groove depth exceeds 1.2, the contact area between the belt and the pulley becomes too small, the transmission force of the belt teeth decreases, and jumping occurs. Therefore, the belt tooth height / pulley groove depth is preferably in the range of 1.00 to 1.20 as shown in FIG.

The toothed belt 1 and the toothed pulley 5 in FIG. 1 have trapezoidal teeth. That is, FIG.
In FIG. 1A, the side surface 3 of the belt tooth portion 2 is formed in a straight line, and in FIG. 1B, the side surface 7 of the pulley groove portion 6 is also formed in a straight line.

FIG. 2 is a cross-sectional perspective view showing an example of the toothed belt according to the present invention. The toothed belt 1 has a plurality of tooth portions 2 along the longitudinal direction of the belt and a core wire 9 between the core wires. A plurality of backs 10 are arranged at a pitch 11 and buried, and a tooth surface 13 is provided.
And the tooth cloth 12 covering the surface of the tooth bottom portion 14.

The rubber used for the tooth portion 2 and the back portion 10 includes chloroprene rubber, natural rubber, millable urethane rubber, hydrogenated nitrile rubber, chlorosulfonated polyethylene (CSM), alkylated chlorosulfonated polyethylene ( Rubbers such as ACSM) are preferred. The hydrogenated nitrile rubber has a hydrogenation rate of 80% or more. In order to exhibit heat resistance and ozone resistance, the hydrogenation rate is 9%.
0% or more is good. A hydrogenated nitrile rubber having a hydrogenation rate of less than 80% has extremely low heat resistance and ozone resistance. In the rubber, as a compounding agent, carbon black, zinc white, stearic acid, a plasticizer, an antioxidant and the like are added,
The vulcanizing agents include sulfur and organic peroxides, but the compounding agents and vulcanizing agents are not particularly limited.

The canvas used as the tooth cloth 12 is 6 nylon, 66 nylon, polyester, aramid fiber or the like, and these may be used alone or in a mixture. The warp yarns (belt width direction) and weft yarns (belt length direction) of the tooth cloth 12 are also filament yarns or spun yarns of the above fibers, and the weaving constitution may be any of plain weave, twill weave, and satin weave. In addition, it is preferable to partially use a stretchable wooly nylon yarn, urethane elastic yarn, or a mixed twist of urethane elastic yarn and nylon as the weft.

Among them, in the case of a plain weave canvas, since the wefts and the warps are alternately layered vertically, the corrugated intersections of the wefts and the warps are formed continuously in the weft and warp directions. on the other hand,
When twill or satin weave is used, weft and warp yarns form multiple wavy intersections each, and there are fewer wavy intersections than normal plain weave, and rubber is not only between yarns but also between intersections. When it is used in the corrugated portion of the belt, the warp yarn and the weft yarn in the belt flexibility can avoid direct contact and improve the belt life, which is preferable.

The above-mentioned tooth cloth 12 is mainly treated with resorcin-formalin-latex liquid (RFL liquid). R
The FL solution is a mixture of latex with an initial condensate of resorcin and formalin, and the latex used here is styrene / butadiene / vinylpyridine terpolymer, hydrogenated nitrile rubber, chlorosulfonated polyethylene, It is a latex such as epichlorohydrin.

In the present invention, the tooth cloth 12 is treated only with the RFL solution, and the amount of the solid content of the resorcin-formalin resin deposited is adjusted to 20 to 50% by weight. It becomes difficult to expand and the rubber of the tooth part is not exposed from the surface, and the scattering of rubber powder can be prevented. In addition, the solid content of the resin adhered to the tooth surface lowers the frictional resistance of the surface, and reduces noise during belt driving.

However, the aramid fiber rope used as the above-mentioned core wire 9 usually has a filament group formed by converging 100 to 400 monofilaments having a denier of 0.5 to 2.0, and one or two of these strands. After 3 to 3 pieces have been aligned, a single twist is performed with a twist number of 0 to 100 times / 10 cm to have a diameter of 0.10 to 0.20 mm. Here, if the monofilament is less than 0.5 denier, the rigidity decreases, but the modulus also decreases, belt elongation occurs, the printing accuracy or conveyance accuracy deteriorates, and the cost increases, while 2.0 Beyond denier, the belt lacks flexibility and increases in rigidity.

Further, when the diameter of the rope is less than 0.10 mm, the modulus becomes low and belt elongation occurs,
Further, the PLD value of the belt becomes too low, resulting in a long meshing with the pulley, which deteriorates printing accuracy or conveyance accuracy. On the other hand, if it exceeds 0.20 mm, the belt is lacking in flexibility and rigidity is increased, and the starting torque is also increased.

The pitch between the core wires is 0.2 to 0.5 m.
Set to m. If the pitch between the cords is less than 0.2 mm, the cords will be heavy and cannot be manufactured at the time of manufacturing the belt. On the other hand, if it exceeds 0.5 mm, the belt modulus becomes low, the belt stretches, and the printing accuracy or conveyance accuracy deteriorates.

The aramid fiber used for the core wire 9 is an aramid having an aromatic ring in the main chain of the molecular structure, for example, trade name Conex, Nomex, Kevlar, Technora,
Twaron and the like.

[0026]

EXAMPLES Examples of the present invention will be further described below. The tooth shape of the belt and pulley was trapezoidal. Belt type is T80 type and belt size is 262T8
0 and the belt width was 2.0 mm. This belt is composed of a warp yarn made of 6 nylon of 80 denier and a weft yarn made of 6 nylon of 80 denier as a lower cover cloth, and has a warp density of 250 (threads / cm) and a weft density of 300 (threads / 5 cm).
After weaving with a twill canvas, the fabric is vibrated in water to shrink it to about half the width at the time of weaving, and then the canvas is RFL.
After being dipped in the liquid and squeezed by a pair of rolls at 0.5 kgf / cm (gauge pressure), the canvas was dipped in the same RFL liquid and squeezed at the same gauge pressure, and then dried to form a tooth cloth. . The resin solid content of the tooth cloth is [weight of treated cloth-weight of untreated sail cloth] / [weight of untreated sail cloth] × 1
It was about 20% with the calculation formula of 00 (%).

Next, a non-twisted multifilament strand is formed by aligning a predetermined number of aramid fiber filaments (trade name: Technora) having a predetermined strand diameter as a core wire, and one strand is twisted 40 times / First twisting (single twist) was performed at 10 cm to prepare a pair of S and Z twisted ropes, which were dipped in an adhesive made of an RFL solution and dried to obtain a treated rope. The structure of the obtained rope is shown in Table 1 below.

Therefore, the tooth cloth was finished into an endless tubular shape and set in a mold. From above, S and Z
A pair of ropes is 0.31 as core pitch examples 1-3.
mm, as Example 4, the core wire pitch is 0.44 mm and the tension is 1.0 kg / piece, and the windings are alternately wound. A belt was produced. Belt size is the number of teeth:
262, tooth pitch: 2.032 mm, and the tooth profile of the belt was trapezoidal T80. The rigidity, starting torque, and relationship between the single pitch difference between the belt and the pulley and the speed variation rate of each of the obtained belts were measured by the following methods. The results are shown in Table 1 below and FIG. 3, respectively. Further, in the measurement of the speed fluctuation rate, the engagement state of the engagement between the belt teeth and the pulley teeth was observed by a high speed video. The state is shown in FIGS. 9 and 10. FIG. 11 shows the relationship between the amount of change in axial separation and the axial load of each belt obtained.

(A) Measuring method of belt rigidity: The cut belt 22 is set on the sample setting table 17 of the bending rigidity measuring machine 15 shown in FIG. 10 teeth from the belt, and the belt-shaped tension gauge 16 is vertically moved to the protruding belt end portion by using the motor 19 and the ball screw 20 to apply a load to bend the protruding belt 21. Read the scale of the flat tension gauge 16 when the belt comes into contact with the one surface 18 of the sample mounting table 17.

(B) Method of measuring starting torque: The driving side pulley 24 (number of teeth 20) fixed on the starting torque measuring machine 23 shown in FIG. 6 and the driven side movable in a room adjusted to a predetermined temperature. The belt 1 is hung on the pulley 25 (having 20 teeth) and the driven pulley 25 is moved to give a tension of 300 gf, and an axial load of 600 gf is applied to the belt. Then, the weight 26 is hung on the passive side pulley 25, the weight is gradually increased, the pulley rotates, and the minimum load W when the weight descends by 5 cm is measured. It is calculated from W−W ₀ ) × 0.65. Note that W ₀ is a load with which the weight descends by 5 cm or more when the belt is not attached.

(C) A method for measuring the relationship between the single pitch difference between the belt and the pulley and the speed fluctuation rate; in the speed fluctuation rate measuring device 27 shown in FIG. 7, the belt 1 is attached to the driving pulley 28 and the driven pulley 29. And the driven pulley 29 is moved to apply a tension of 300 gf to the belt.
Apply 0 gf of axial load, then drive side pulley 28 to 45
Rotate at 0 rpm and check if the dynamic shaft load is 600 gf. After the axial load stabilizes at the specified value,
Speed unevenness is measured with the speed unevenness measuring device 30, and FFT3
At 1, the speed fluctuation rate (wow and flutter) is calculated. 3
2 indicates a sensor.

In Examples 1 to 3, the belt single pitch was fixed at 2.032 mm, and in Example 1, the pulley outer diameter was 6.09 mm (single pitch 2.072 mm).
That is, the single pitch difference is -0.04 mm, and the pulley outer diameter is 6.02 mm (single pitch 2.052 m as Example 2).
m), that is, a single pitch difference of -0.02 mm, and as Example 3 the pulley outer diameter is 5.99 mm (single pitch 2.042 mm), that is, a single pitch difference of -0.01.
mm.

On the other hand, as a comparative example, the belt single pitch is fixed at 2.032 mm, and as the comparative example 1, the pulley outer diameter is 6.15 mm (single pitch 2.092 mm), that is, the single pitch difference is −0. As a comparative example 2, the outer diameter of the pulley was 5.93 mm (single pitch 2.022 mm), that is, the single pitch difference was 0.01 mm.

A non-contact speed unevenness measuring device utilizing the Doppler effect of laser light was used as the speed unevenness measuring device for measuring the speed fluctuation ratio. It is defined by the following equation as a percentage of the variation ΔV of the rotation speed with respect to the specific rotation speed V ₀ . Speed fluctuation rate (Wow and flutter) = (ΔV / V ₀ ) × 10
0 (%) The shift variation rate between the belt and each pulley was measured as described above. The result is shown in FIG. Further, the results of observing the meshing state of the engagement between the belt teeth and the pulley groove at the time of measuring the speed variation rate with a high-speed video are shown in FIG. 9 for Example 2 and FIG. 10 for Comparative Example 2. 9 (a) to 10 (d)
In the engagement between the belt tooth and the pulley groove, the belt tooth side surface from the start of tooth engagement to the complete engagement,
It is the figure which observed the change of the state of meshing with the pulley groove side by a high-speed video.

From these results, in the toothed belt drive device of the embodiment, the speed fluctuation rate is 1.5% or less, whereas in the comparative examples 1 and 2, it exceeds 1.7%. , Which is a low number. When the speed fluctuation rate exceeds 1.7%, the printing accuracy and the transportation accuracy are deteriorated. Therefore, the toothed belt drive device of the embodiment has an effect of improving the printing accuracy and the transportation accuracy. Moreover, from FIG. 9 and FIG.
Compared with the meshed state of Comparative Example 2, the meshed state of No. 2 shows less interference between the belt tooth side surface and the pulley groove side surface, and shows a smooth meshed state. The smoothness of this engagement has the effect of reducing fluctuations in speed.

Comparative Examples 3 to 4 Glass fiber filaments having a diameter of about 9 μm were bundled as a core wire to form a strand. The strand was immersed in RFL liquid and dried at 250 ° C. for 2 minutes, and then a predetermined number was collected. A rope having a twist of 4.0 times / 10 cm was obtained. Rope configuration is ECG-150-3 / 0 (diameter 0.25mm)
And ECG-150-2 / 0 (0.2 mm diameter). Except for the core wire, there is no difference from the embodiment. The rigidity and starting torque of each of the obtained belts at each temperature were measured by the method described above. The above results are summarized and the results are shown in Table 1.

[0037]

[Table 1] Below margin

From the above results, it can be seen that the belt of the example maintains a low belt rigidity even at a low temperature of -35 ° C. and the starting torque is smaller than that of the comparative example. Further, from the relationship between the axial deviation change amount and the axial load in FIG. 10, the belt elongation of Example 4 is larger than that of Examples 1 to 3, and when the core pitch exceeds 0.5 mm, the belt modulus becomes low. It can be seen that the belt stretches and print accuracy or conveyance accuracy deteriorates. Therefore, by setting the core pitch of the belt of the present invention to 0.2 to 0.5 mm, the belt itself is soft and supple within a range that does not adversely affect the printing accuracy or the conveyance accuracy even at room temperature and low temperature atmosphere. In addition, the tension at low temperature is reduced, the starting torque can be reduced, the load on the shaft can be reduced, and the electric capacity of the small motor can be reduced.

Next, in order to know the proper relationship between the belt tooth height and the pulley groove depth, the belt size; 210ST1.
0-6.4 (a round tooth belt with a tooth pitch of 1.0 mm, a number of teeth of 210, and a width of 6.4 mm), pulley teeth; 20 teeth have different ratios of belt tooth height and pulley groove depth, Rotation speed 450r. p. The test was conducted at m, and the rate of change in speed was measured using the same tester as described above. The result is as shown in FIG. 4, and the belt tooth height / pulley groove depth of 1.06 has a much smaller speed fluctuation rate than those of 1.0 and 1.23 and is effective. It is discovered that there is.

[0040]

As described above, in the present invention, the difference in the single pitch between the belt teeth and the pulley groove is limited to -0.04 to 0 mm,
Preferably, by limiting to -0.02 to 0 mm, the belt speed fluctuation rate can be minimized, and the printing accuracy or conveyance accuracy can be dramatically improved. Above all, by setting the belt tooth height / pulley groove depth = 1.00 to 1.20 in the range, the speed variation rate can be more effectively reduced. Further, as the core wire, a thin aramid rope having a diameter of 0.10 to 0.20 mm is formed by bundling at least one filament group in which aramid fibers made of monofilament having a denier of 0.5 to 2.0 are bundled into one strand. Use, and pitch between cores is 0.2 to 0.5 mm
As a result, the belt itself is soft and supple even at room temperature and low temperature, and has little elongation. Also, since the linear expansion coefficient of aramid fiber is negative, the tension at low temperature is reduced and the starting torque is small. The load on the shaft can be reduced, and the electric capacity of the small moke can be reduced. Further, by treating only the RFL solution as the tooth cloth, the opening of the tooth cloth is small, and it is difficult for the tooth cloth to expand, the rubber of the tooth portion is not exposed from the surface, and the scattering of the rubber powder can be prevented. Further, the solid content of the resin adhered to the tooth surface has the effect of reducing the frictional resistance of the surface and reducing the noise when the belt is driven.

[Brief description of the drawings]

FIG. 1 is a partial side view of a belt and a pulley of a toothed belt drive device according to the present invention, where (a) shows a belt and (b) shows a pulley.

FIG. 2 is a perspective view of a main part of the toothed belt according to the present invention.

FIG. 3 is a diagram showing a relationship between a single pitch difference between a belt tooth and a pulley groove of a toothed belt drive device according to the present invention and a speed variation rate.

FIG. 4 is a diagram showing a relationship between a belt tooth height and a pulley groove depth in a toothed belt drive device according to the present invention and a speed variation rate.

FIG. 5 is a view showing a bending rigidity measuring device for a toothed belt according to the present invention.

FIG. 6 is a view showing a starting torque measuring device for a toothed belt according to the present invention.

FIG. 7 is a diagram showing a speed variation rate measuring device for a toothed belt according to the present invention.

FIG. 8 is a diagram showing a definition of a speed fluctuation rate (wow and flutter).

FIG. 9 is a toothed belt drive device according to the present invention, which is Embodiment 2
6A to 6D are diagrams showing the meshing state of the engagement between the belt teeth and the pulley groove at the time of measuring the speed fluctuation rate of FIG.

FIG. 10 is a diagram showing a meshing state in engagement between a belt tooth and a pulley groove at the time of measuring a speed variation rate in Comparative Example 2 in the toothed belt drive device according to the present invention, and (a) to (d) of FIG. It is a transition of the same meshing state.

FIG. 11 is a diagram showing a relationship between an axial separation change amount and an axial load of the toothed belt according to the present invention.

FIG. 12 is a partial side view showing a polygonal meshing state of a belt tooth and a pulley groove in a conventional toothed belt drive device.

[Explanation of symbols]

 1 Toothed Belt 2 Belt Tooth Part 3 Belt Tooth Part Side 4 Belt Tooth Single Pitch 5 Pulley 6 Pulley Groove 7 Pulley Groove Side 8 Pulley Groove Single Pitch 9 Core 10 Back 11 Pitch 12 Tooth Cloth 15 Belt Bending Rigidity measuring machine 16 Ogi-type tension gauge 17 Specimen mounting table 19 Motor 20 Ball screw 23 Starting torque measuring machine 24, 28 Driving pulley 25, 29 Driven pulley 26 Weight 27 Speed fluctuation rate measuring device 30 Speed unevenness measuring machine 31 FFT 32 Sensor

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Akira Kawaguchi 4-1-21, Hamazoe-dori, Nagata-ku, Kobe Mitsuboshi Belt Co., Ltd. (72) Hiroyuki Nishio 4-1-2-1, Hamazoe-dori, Nagata-ku, Kobe Inside Mitsuboshi Belting Co., Ltd. (72) Hideaki Tanaka 4-1-21, Hamazoe-dori, Nagata-ku, Kobe Mitsuboshi Belting Co., Ltd.

Claims (8)

[Claims] 1. In a drive device in which a toothed belt is wound around at least a pair of toothed pulleys to perform a reciprocating motion or a one-way motion, a single pitch difference between a belt tooth and a belt pulley groove is -0.04. A toothed belt drive device characterized in that the fluctuation of the belt speed is reduced by setting the range of 0 mm. 2. The relationship between the belt tooth height and the pulley groove depth of the toothed belt drive device is expressed as belt tooth height / pulley groove depth =
2. The toothed belt drive device according to claim 1, which is 1.00 to 1.20. 3. The toothed belt driving device according to claim 1, wherein the belt teeth and the pulley groove of the toothed belt driving device are trapezoidal. 4. The core wire embedded in the belt main body of the toothed belt used in the toothed belt drive device is 0.5 to 2.
The tooth according to claim 1, 2 or 3, which is an aramid fiber rope having a diameter of 0.10 to 0.20 mm obtained by bundling at least one filament group in which aramid fibers composed of 0 denier monofilaments are bundled and twisted. Belt drive device. 5. The toothed belt drive device according to claim 1, wherein the pitch between the cords embedded in the belt body of the toothed belt to be used is in the range of 0.2 to 0.5 mm.
2. The toothed belt drive device according to 2, 3, or 4. 6. In a toothed belt driving device, a tooth cloth coated on the surface of a belt tooth portion of a toothed belt to be used is treated only with resorcin-formalin-latex liquid, and rubber of the tooth portion is discharged from an opening portion of the canvas. The toothed belt drive device according to claim 1, 2, 3, 4, or 5, which is not exposed. 7. A drive device for reciprocating or unidirectionally wrapping a toothed belt between at least a pair of toothed pulleys, wherein belt tooth height / pulley groove depth is 1.00.
Aramid comprising a monofilament having a single pitch difference between the belt tooth and the pulley groove of -0.02 to 0 mm and a core of the belt main body of 0.5 to 2.0 denier. A diameter of 0.1 obtained by bundling at least one or more filaments bundled with fibers
An aramid fiber rope having a length of 0 to 0.2 mm, a pitch between cords of 0.2 to 0.5 mm, and a tooth cloth coated on the surface of the belt tooth portion is treated only with a resorcin-formalin-latex liquid. A toothed belt drive device characterized in that the rubber of the tooth portion is not exposed from the opening of the canvas. 8. An aramid fiber comprising a monofilament having a denier of 0.5 to 2.0 denier, which is obtained by bundling at least one or more of a bundle of aramid fibers bundled and twisted.
An aramid fiber rope having a diameter of 0.10 to 0.20 mm and a pitch between core wires of 0.2 to 0.5 mm,
A toothed belt characterized in that the tooth cloth covered on the surface of the tooth portion of the belt is treated only with a resorcin-formalin-latex liquid so that the rubber of the tooth portion is not exposed from the opening of the canvas.