KR20000047850A - Belt conveying method, and conveying belt and belt conveying apparatus for applying this method - Google Patents

Abstract

PURPOSE: A method of belt transmission is provided to increase a torque by preventing a problem that a tooth of the belt 2 is out of mesh with the pulley 4 (hereinafter referred to as "the tooth-out-of-mesh problem") in transmitting to a driven portion a rotational force of the toothed belt to be engaged in the toothed pulley on the driving shaft. CONSTITUTION: A method of belt transmission wherein a rotational force of a toothed belt (2) to be engaged in a toothed pulley (4) on a driving side is transmitted to a driven portion, the method being characterized in that the belt (2) is covered with a tension-bearing belt (1) having a high tensile strength to make ready to transmit a frictional force in order that the tension is transmitted to the driven portion through the belt, thereby increasing torque and preventing a problem that a tooth of the toothed belt is out of mesh with the toothed pulley.

Description

BELT CONVEYING METHOD, AND CONVEYING BELT AND BELT CONVEYING APPARATUS FOR APPLYING THIS METHOD}

The present invention relates to a belt transmission method such as a timing belt, an electric belt and a belt transmission apparatus for carrying out this method.

Conventionally, the timing belt is used for the transmission of the driving force which is quiet and a slip is not produced. As for the transmission by this timing belt, as shown in FIG. 1, the toothed pulley 4 is attached to the drive shaft 41 and the driven shaft 42, respectively, and the looped toothed belt 2 is attached. ) Is meshed with the toothed pulley 4 for transmission.

In this case, in accordance with the rotation of the toothed pulley 4 of the drive shaft 41, the rotational force is transmitted to the toothed pulley 4 of the other driven shaft 42 via the toothed belt 2. It is delivered. Since the toothed belt 2 is usually made of an elastic member having a predetermined hardness such as synthetic resin, noise is not generated in the engagement portion of the toothed pulley 4 and the toothed belt 2. There is an advantage. Furthermore, since the toothed portion of the toothed belt 2 and the toothed pulley 4 are engaged and the driving force is transmitted, no slippage is generated such as a normal flat belt, so that the rotation angle or movement distance of the drive shaft is reduced. There is an advantage that can be accurately delivered to the i-side.

By the way, with this conventional timing belt, the transmission torque from the drive shaft 41 to the driven shaft 42 does not become large. Since the toothed belt 2 is made of the same material as described above, the toothed belt 2 is caused by the tension generated in the toothed belt 2 rotated between the toothed pulley 4 and rotated. This is because elongation is generated in this step, and the transmission torque decreases corresponding to the elongation.

In addition, in order to raise this transmission torque, the structure which uses several twisted pair | wire 21 as a core wire as the toothed belt 2 as shown in FIG. 2 is employ | adopted. It may become. The stranded wire 21 is a stranded wire made of a steel cord or an aramid fiber cord. Since the stranded wire 21 bears a tension, the tensile strength is increased and the transmission torque is increased as compared with that in which these core wires are not mounted. By the way, even if such a core wire is used, elongation tends to occur in the stranded wire 21, and when the transmission torque is large, the toothed portion 22 of the toothed pulley 4 and the toothed belt 2 is provided. The phenomenon of tooth skipping occurs between. In order to alleviate this tooth skipping, in the toothed belt 2, a plurality of rollers 30 are arranged at predetermined intervals on the outer circumference of the portion wound around the toothed pulley 4, and the toothed type The belt 2 is slightly improved by being pushed toward the toothed pulley 4 side. However, according to the method of using the roller 30, the transmission torque is about 7.5 kgf · m (a case of a timing belt having a length of about 5 m in a width of 25 mm, and a pulley diameter of 60 mm).

An object of the present invention is to suppress the skipping of teeth and increase the transmission torque when the rotational force of the toothed belt engaged with the toothed pulley on the drive shaft side is transmitted to the driven part.

Another object of the present invention is to provide a transmission belt that can easily achieve the above object.

Another object of the present invention is to provide a method for suppressing tooth skipping and increasing transmission torque when the rotational force of the toothed belt engaged with the toothed pulley on the drive shaft side is transmitted to the driven part. It is to provide a belt transmission device that can be easily performed.

1 is an explanatory diagram of a conventional example;

2 is an explanatory diagram of an improvement plan of a conventional example;

3 is an explanatory diagram of Embodiment (1) of the present invention;

4 is a partial cross-sectional view of FIG.

5 is a perspective view of a tension bearing belt 1 used in the second embodiment;

6 is an explanatory diagram of a motorized state of a second embodiment;

7 is an explanatory diagram of a modification of the tension burden belt 1 of this example;

8 is an explanatory diagram of a modification of the toothed belt 2;

9 is an explanatory diagram of another embodiment of the electric belt of the present invention;

10 is an explanatory diagram of still another embodiment of the electric belt;

11 is an overall plan view of Embodiment 3 of the present invention;

12 is a side view of FIG. 11,

FIG. 13 is an explanatory view of the belt transmission of the main parts of FIGS. 11 and 12;

FIG. 14 is a view corresponding to FIG. 13, and is an explanatory view in the case of any tension-bearing belt 1 of the connecting portion 13.

15 is an explanatory diagram of another example of the interval adjusting mechanism 5;

16 is an explanatory diagram of an example of a gap adjusting mechanism 5 operated manually; and

17 is an explanatory diagram of another example of a rocking arm electric motor.

(Explanation of the sign)

(1): tension bearing belt (2): toothed belt

(4): toothed pulley

In the drawings, the same reference numerals indicate the same or equivalent parts.

The technical means of the first invention, which has been devised to attain the above object, is a method for transmitting the rotational force of the toothed belt 2 engaged with the toothed pulley 4 on the driving side to the driven part. A belt transmission method for covering the outer circumferential surface of the toothed belt (2) with a tension-bearing belt (1) having a high tensile force in a frictional force transmission state, and transmitting tension to the other driven part through the tension-bearing belt (1). To provide.

Here, the frictional force transmission state includes a case where the frictional force transmission state is joined in an electrically driven state (a state in which no sliding occurs) by adhesion.

The toothed belt 2 and the toothed pulley 4 are engaged in the same manner as the conventional one. In addition, the tension-bearing belt 1 and the toothed belt 2 are coupled in an electrically driven state by a frictional force. Since the tension-bearing belt 1 is a material having a large pulling force, the rotational force of the toothed pulley 4 on the drive side is reliably converted into the tension of the tension-bearing belt 1 through the frictional force with the toothed belt 2. . Since the elongation in this tension burden belt 1 hardly occurs, the efficiency which is converted into the said tension of the rotational force is high.

On the other hand, the tension-bearing belt 1 is an aspect which covers the outer circumferential surface of the toothed belt 2 wound around the toothed pulley 4, and furthermore, since the tensioning belt is large, the toothed belt 2 When the tooth part of the () becomes a tendency to skip a tooth, the tension-bearing belt 1 fastens the engagement part of the toothed belt 2 over the whole so as to prevent this tooth skipping. This makes it difficult to generate tooth skipping.

The second technical means of the present invention, which has been devised in order to achieve the above-described second object, includes the " toothed belt 2 engaged with the toothed pulley 4 and the toothed belt 2 ". To provide an electric belt composed of a tension-bearing belt (1) having a large tensile force coated in a frictional force transmission state.

In this transmission belt, since the transmission belt is caught and rotated between the toothed pulley 4 on the driving side and the toothed pulley 4 on the driven side, the same problem as in the first invention is solved and the same effect is achieved. Is exerted. Moreover, implementation of said 1st invention is performed very simply.

In the case where the driven side is a driven portion that moves linearly, the tension-bearing belt 1 may be connected to the driven portion.

The third technical means of the present invention, which has been devised to attain the above-mentioned third object, is, "The toothed pulley 4 on the driving side and the toothed pulley 4 on the driven side mesh with them. A belt transmission device driven by an attachable belt (2), wherein an idle roller (3) external to the toothed belt (2) is provided between the pair of toothed pulleys (4). The tensioning belt 1 is provided freely, and a tension-bearing belt 1 externally provided in a frictional force transmission state is provided on the outer circumferential surface of the toothed belt 2 engaged with each toothed pulley 4. It is to provide a belt transmission device wherein the idle roller (3) is provided inside the running portion of the tension-bearing belt (1) between the toothed pulley (4).

Here, the frictional force transmission state means that the frictional force generated when the tension-bearing belt 1 is pressed against the surface of the toothed belt 2 acts between the toothed belt 2 and the tension-bearing belt 1. A part of torque or tension is transmitted between the toothed belt 2 and the tension bearing belt 1.

The toothed belt 2 and the toothed pulley 4 are engaged in the same manner as the conventional one, but the idler roller 3 is circumscribed to the running portion of the toothed belt 2 between the toothed pulleys. In this part, therefore, the toothed belt is bent inward. Since the idle roller 3 is provided in the bent portion, and the idle roller 3 is provided inside the running portion of the tension bearing belt 1, the tension bearing belt 1 and the idle roller 3 are in a non-contact state. have. In addition, the tension-bearing belt 1 and the toothed belt 2 are coupled in an electrically driven state by a frictional force. Since the tension-bearing belt 1 is a material having a large pulling force, the rotational force of the toothed pulley 4 on the drive side is reliably converted into the tension of the tension-bearing belt 1 through the frictional force with the toothed belt 2. . Since the elongation in the tension-bearing belt 1 hardly occurs, the conversion efficiency of the rotational force to the tension is high.

On the other hand, since the tension-bearing belt 1 is in a state of externally engaging the outer peripheral surface of the toothed belt 2 engaged with the toothed pulley 4 and fastening the toothed belt, the tensioning force is large. The saw tooth skipping of the tooth part of the toothed belt 2 is suppressed.

When the toothed belt 2 is extended, the position of the idler roller 3 is adjusted so that the tension of the toothed belt 2 is adjusted to an appropriate value.

Since the rotational force of the toothed pulley 4 on the drive side is effectively converted to the tension of the tension-bearing belt 1, and the elongation of the tension-bearing belt 1 due to tension is hardly generated, The tension transfer efficiency is improved as compared with the conventional one, and the work such as the minute adjustment of the pulley interval, which is conventionally performed to absorb the elongation of the belt, is also unnecessary.

In addition, since the tooth jump of the toothed belt 2 is unlikely to occur, a deviation is unlikely to occur between the rotational amount of the toothed pulley 4 and the operation amount of the driven side corresponding thereto. Even when the toothed belt 2 extends, the tension can be maintained at an appropriate value by adjusting the tension by the idle roller 3.

The above and other objects, features, and advantages of the present invention will be more clearly understood by reading the following detailed description and the accompanying drawings.

Embodiment of the Invention

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described with the example which shows.

(Embodiment 1)

Embodiment 3 shown in FIG. 3, FIG. 4 is employ | adopted by the transmission system which transmits torque from the drive shaft 41 to the driven shaft 42, and the toothed pulley 4 attached to the drive shaft 41, Between the toothed pulley 4 attached to the driven shaft 42, it is a structure installed in tension in the state which wound the transmission belt provided with the driven shaft 42.

As shown in FIG. 3, the transmission belt follows the smooth surface portion 23 on the opposite side of the toothed portion 22 of the looped toothed belt 2, and similarly bears the tension of the looped shape. It is the structure which arrange | positioned the belt 1, and is not joined with the toothed belt 2 and the tension burden belt 1 by this, but it wound around the pair of toothed pulley 4 mentioned above. The tension-bearing belt 1 is similarly wound to cover the outer circumferential surface of the toothed belt 2.

In this example, the toothed belt 2 is a general so-called timing belt having a total thickness of 4.5 mm and a width of 25 mm. On the other hand, the tension-bearing belt 1 has a plate thickness of 0.15 to 0.25 mm with the same width. The steel belt of maraging steel is used.

The loop length of the steel belt is set to a predetermined value based on the diameter of the pitch circle of each toothed pulley 4, the thickness of the toothed belt 2, and the like. The tensile strength of the steel belt is set at 375 to 625 kgf (15 to 25 kgf / mm per unit width).

When the above transmission belt is used, the torque transmitted from the drive shaft 41 on the drive side to the driven shaft 42 on the driven side is greatly increased. When the limit torque was exceeded, a slip occurred between the toothed belt 2 and the tension bearing belt 1, but as in the prior art, a tooth skipping phenomenon that does not include the tension bearing belt 1 is not generated. Did. Moreover, compared with the transmission torque at the time of the tooth skip phenomenon in this conventional case (maximum transmission torque: 7.5 kgf * m), the transmission torque at the time of the said sliding | sliding to the tension burden belt 1 became large. . The torque that can be transmitted has been improved by twice compared to the case of the conventional toothed belt 2 alone.

In this example, as shown in FIG. 4, the tension-bearing belt 1 is attached to the smooth surface portion 23 in a frictional engagement state. In order to increase this frictional engagement, FIG. As shown in FIG. 6, a configuration in which a plurality of through holes 11 are formed in the tension-bearing belt 1 and these through holes 11 are continuous in the longitudinal direction may be adopted. Using this example, the frictional engagement is improved by the peripheral edge of the through hole 11 encroaching on the smooth surface portion 23.

The through hole 11 may be a burring hole as shown in FIG. 7. In this case, the height H of the standing portion 12 of the burring hole is preferably about the thickness of the tension-bearing belt 1 (about 0.15 to 0.25 mm).

The smooth surface part 23 and the tension burden belt 1 may be integrally joined by adhesion, as shown in FIG.

In addition to the above configuration, as shown in FIG. 8, the convex 29 is integrally formed on both sides of the smooth surface portion 23 in the cross section of the toothed belt 2. It can also be set as the structure. For the toothed belt 2 trimmed into the cross-sectional shape provided with the convex 29 in advance as shown in the same drawing, the loop-shaped tension-bearing belt 1 of the length fitted thereto is It is a structure used by the aspect which coat | covered the outer side. In this case, when the electric belt is used and the electric driving is performed, the tension-bearing belt 1 is always held between the protrusions 29 and 29 to travel in a position where it is positioned. The belt 1 does not escape from the toothed belt 2. Therefore, the stability of the electric torque and its operation is ensured.

(Embodiment 2)

In the first embodiment, the case where the torque is transmitted from the drive shaft 41 with the toothed pulley 4 to the driven shaft 42 with the toothed pulley 4 has been described as an example. As a configuration, a reciprocating rotation of a certain angle may be transmitted. For example, a toothed belt 2 of a predetermined length is wound around the toothed pulley 4, and both ends of the tension-bearing belt 1 wound around the outer circumference of the toothed belt 2 are linearly reciprocated. What is necessary is just to set it as the structure attached to the to-be-powered part 2.

This is transmitted to the tension-bearing belt 1 via the toothed pulley 4 by a reciprocating rotation of one drive shaft 41 at a predetermined angle, and the driven part with both ends of the tension-bearing belt 1 attached thereto. (2) moves in a straight line.

(etc)

In the above embodiment, although the steel belt is employed as the tension bearing belt 1, a band-shaped sheet made of carbon fibers or aramid fibers may be used other than the steel belt. Also in this case, the tensile strength is preferably about 15 kgf / mm to 25 kgf / mm per unit width, and in this case, the transmission torque range of 11.2 kgf · m to 18.7 kgf · m (for pulley diameter 60mm) is usually used. Used. This value is 1.5 to 2.5 times that of the conventional timing belt. Moreover, durability under these use conditions is sufficient.

In order to ensure accurate angular transfer, it is necessary to set the transmission torque largely (2.2 to 2.5 times the transmission torque in the conventional case), and in that case, the setting force per unit width is set to about 22 kgf / mm to 25 kgf / mm. do.

Moreover, you may employ | adopt the toothed belt of a core wire insertion as the toothed belt 2 of each said embodiment.

As a tooth type of the toothed pulley 4 and the toothed part 22, of course, conventionally known teeth can be employed. For example, it is also possible to use circular teeth.

In addition, the transmission belt of the said embodiment uses the combination of the toothed belt 2 and the tension burden belt 1 of this invention to the toothed pulley 4 provided in the self-propelled drive part 39 like FIG. As shown in FIG. 10, both ends of the toothed belt 2 and the tension-bearing belt 1 are connected to the driven part 31 attached to the pair of guide shafts 38. It is also used in a transmission method in which the transmission belt is wound around the toothed pulley 4 attached to the drive shaft 41 and the toothed pulley 4 attached to the driven shaft 42.

(Embodiment 3)

The belt transmission device of this embodiment is used for the rocking arm of the product extraction robot from an injection molding machine, as shown to FIG. 11, FIG.

The rocking arm is rotated at the tip of the first arm 63 and the first arm 63 attached to the main shaft 62 which rotates freely with respect to the sun gear 61 fixed to the frame 6. And a clamping click 651 connected to a driven arm 42 freely rotatably supported at the distal end of the second arm 64 and clamping a click 651 for holding the resin molded part. The third arm 65.

At the distal end of the first arm 63 there is a planetary gear 66 that meshes with the sun gear 61 through an intermediate gear 611, and an intermediate shaft 411 to which the planetary gear 66 is attached. The silver penetrates through the first arm 63 and is fixed to the second arm 64, which rotates integrally with the intermediate shaft 411. The toothed pulley 4, which is freely engaged with the external shaft relative to the intermediate shaft 411, is fixed to the first arm 63. Thus, in this example. The shaft on the drive side is a fixed shaft.

A driven toothed pulley 4 is attached to a lower end of the driven shaft 42 provided at the tip of the second arm 64, and the driven toothed pulley 4 is fixed to the driven side. The toothed pulley 4 on the side is belt-driven.

The fixed toothed pulley 4 and the belt for driving the toothed pulley 4 attached to the driven shaft 42 have a looped toothed belt 2 as shown in FIG. 13. The loop-shaped tension-bearing belt 1 is similarly arranged along the smooth surface portion 23 on the opposite side of the toothed portion 22 of the toothed portion 22. This includes the toothed belt 2 and the tension-bearing belt ( Although 1) is not joined, the tension bearing belt 1 is externally joined to the outer circumferential surface of the toothed belt 2 engaged with the pair of toothed pulleys 4.

In this example, the toothed belt 2 adopts a general so-called timing belt having a total thickness of 4.5 mm and a width of 25 mm. On the other hand, the tension-bearing belt 1 has a plate thickness of 0.15 to 0.25 in the same width. In mm, a steel belt of mar aging steel is used.

The loop length of the steel belt is set to a predetermined value based on the diameter of the pitch circle of each toothed pulley 4, the thickness of the toothed belt 2, and the like. The tensile strength of is set at 375 to 625 kgf (15 to 25 kgf / mm per unit width).

A pair of idle rollers 3 are provided between the toothed pulleys 4, and the traveling path of the toothed belt 2 is bent by the idle rollers 3, and in this example, The distance between the pair of idle rollers 3 is adjusted by the gap adjusting mechanism 5 attached to the second arm 64.

The interval adjusting mechanism 5 of this example includes a crank 51 in which the idle roller 3 is rotatably held, a crankshaft 52 rotatably held relative to the second arm 64, and the crankshaft. A lever 53 extending from the upper end of the 52, a retraction shaft 54 for reciprocating the tip of the lever 53 in the longitudinal direction of the second arm 64, and a retraction drive 54 for the retraction shaft 54. Servo motor 55 and a feed screw mechanism 56 for converting the rotational force of the servo motor 55 into linear motion.

As for the space | interval control mechanism 5, the front-end | tip part of each lever 53 which cooperates with the crank 51 with each idle roller 3 intersects symmetrically above the 2nd arm 64, and this intersection There is a long hole 531 in the part, and a pin 541 provided at the tip of the advancing shaft 54 is fitted into these long holes 531. Therefore, when the retreat shaft 54 advances and retreats by the operation of the servomotor 55, the pair of levers 53 rotate in accordance with this, so that the crank 51 rotates in accordance with this rotational movement angle, The idle rollers 3 in the eccentric position with respect to the crankshaft 52 approach each other or vice versa apart. As a result, the mutual spacing of the pair of idle rollers 3 is adjusted.

In the ejection robot of this embodiment, the main shaft 62 is the driven shaft 42 of the main servomotor 60 for swinging the arm of the said structure, and the reduction gear 67 which electrically transmitted. Therefore, when this main servomer 60 rotates reciprocally, the 1st arm 63 will be rocked according to this rotation, and the intermediate shaft 411 will rotate by the action of the planetary gear 66, and the 2nd arm ( 64) oscillate for this rotation angle. The driven shaft 42 is adapted to this transmission ratio by mutual transmission of the toothed pulley 4 fixed to the tip of the first arm 63 and the toothed pulley 4 attached to the driven shaft 42. The third arm 65 attached to the rocker swings in accordance with the rotation angle of the driven shaft 42. In this manner, the third arm 65 is oscillated by a predetermined angle in such a manner as to cooperate with the first arm 63 and the second arm 64 in accordance with the reciprocating rotation of the main servomotor 60.

In this case, in the transmission from the toothed pulley 4 of the intermediate shaft 411 to the toothed pulley 4 of the driven shaft 42, the torque transmitted is greatly increased as compared with the prior art. When the limit torque is exceeded, slippage occurs between the toothed belt 2 and the tension-bearing belt 1, but as in the prior art, a tooth skipping phenomenon such as not including the tension-bearing belt 1 occurs. Did not do it. Moreover, compared with the transmission torque (maximum transmission torque: 7.5 kgf * m) at the time of the tooth skip phenomenon in this conventional case, the transmission torque at the time of the said sliding | sliding to the tension burden belt 1 became large. . In particular, since the tension of the toothed belt 2 can be increased by using a pair of idle rollers 3, the limit torque is increased.

In addition, in this example, as shown in FIG. 13, the tension bearing belt 1 is provided in the frictional engagement state with respect to the smooth surface part 23, In order to raise this frictional engagement, it is mentioned above. As shown in Figs. 5 and 6, a configuration in which a plurality of through holes 11 are formed in the tension-bearing belt 1 and these through holes 11 are continuous in the longitudinal direction can be adopted. . Using this example, the frictional engagement is improved by the peripheral edge of the through hole 11 encroaching on the smooth surface portion 23.

The through hole 11 may be a burring hole as shown in FIG. 7. In this case, the height H of the standing portion 12 of the burring hole is preferably about 0.15 to 0.25 mm of the thickness of the tension-bearing belt 1.

In addition, since the tension of the running part can be increased by adjusting the distance between the pair of idle rollers 3, the toothed belt 2 is not stretched to the tension-bearing belt 1, When elongation is generated in the mold belt 2, the tension of the toothed belt 2 can be maintained at a predetermined value by the gap adjustment in accordance with this elongation.

(etc)

In the above embodiment, the toothed belt 2 and the tension-bearing belt 1 of the closed loop are attached to the driven shaft 42 from the toothed pulley 4 fixed to the supporting portion of the intermediate shaft 411. The case where the torque is transmitted to the toothed pulley 4 has been described as an example. Not limited to this, in the case of transmitting a reciprocating rotation of a predetermined angle, for example, a part of the driven toothed pulley 4 is missing, and the banded toothed belt 2 and the tension bearing belt ( 1) as an open loop, both ends may be fixed to the driven toothed pulley 4 by a screw fixing method or the like, and as shown in Fig. 14, only the tension-bearing belt 1 is provided. It is also possible to employ a method in which the ends are connected in a band shape by the connecting portions 13 which are screwed or caulked.

In addition, as shown in FIG. 17, when the 2nd arm 64 is made into the fixed arm, and the 3rd arm 65 attached to the front-end | tip is made into the structure which oscillates, it is made to electrically rotate with the cylindrical shaft 62. FIG. While the drive shaft 41 is freely supported by the second arm 64 for rotational movement, a toothed pulley 4 on the drive side is attached to the drive shaft 41, and the toothed pulley on the drive side. (4) is geared with the toothed pulley (4) of the driven shaft (42). This causes the third arm 65 on the driven side to swing in accordance with the rotation of the main shaft 62.

In addition, the crank of the spacing adjusting mechanism 5 and the transmission mechanism of the servomotor 55 have a configuration in which the crankshaft 52 rotates symmetrically by gear transmission as shown in FIG. The gear 55 may be gear-driven. Moreover, as shown in FIG. 16, the space | interval of the front-end | tip of the lever 53 extended from the crankshaft 52 may be adjusted by the turnbuckle mechanism 59. As shown in FIG. In this case, the gap can be controlled by rotating the nut barrel 58 constituting the turnbuckle mechanism 59.

In the said embodiment, although the steel belt was employ | adopted as the tension burden belt 1, you may use the band-shaped sheet which consists of carbon fiber and aramid fiber other than this steel belt. Also in this case, the tensile strength is preferably about 15 kgf / mm to 25 kgf / mm per unit width, and in this case, at a transmission torque range of 11.2 kgf · m to 18.7 kgf · m (for a pulley diameter of 60 mm) which is usually used. Used. This value is 1.5 to 2.5 times that of the conventional timing belt. In addition, durability under these use conditions is sufficient. In addition, the outer surface of the tension-bearing belt 1 may be coated with the constituent material of the toothed belt 2.

In order to ensure accurate angular transfer, it is necessary to set the transmission torque largely (2.2 to 2.5 times the transmission torque in the conventional case), and in this case, the tensile force per unit width is set to about 22 kgf / mm to 25 kgf / mm.

Moreover, you may employ | adopt the toothed belt inserted with the core wire as the toothed belt 2 of said each embodiment.

It goes without saying that the teeth of the toothed pulley 4 and the toothed part 22 can be employed conventionally known teeth. It is also possible to use circular teeth, for example.

The present invention has the following peculiar effects due to the above-described configuration.

Since the rotational force of the toothed pulley 4 on the drive side is efficiently converted to the tension of the tension-bearing belt 1, and the extension of the tension-bearing belt 1 due to tension is hardly generated, therefore, to the driven portion. The tension transfer efficiency is improved as compared with the conventional one, and the work such as the minute adjustment of the pulley spacing, which is conventionally performed to absorb the elongation of the belt, is also unnecessary.

In addition, since tooth skipping of the toothed pulley 4 and the toothed belt 2 is unlikely to occur, the amount of rotation between the toothed pulley 4 and the amount of operation on the side of the driven part corresponding thereto is reduced. It is hard to produce a deviation.

Claims (17)

In the method of transmitting the rotational force of the toothed belt 2 engaged with the toothed pulley 4 on the driving side to the driven part, a tension-bearing belt having a large tensile force on the outer circumferential surface of the toothed belt 2. (1) is coated in a frictional force transmission state, and the belt transmission method characterized in that the tension is transferred to the other driven portion through the tension-bearing belt (1). 2. The tension-bearing belt (1) according to claim 1, wherein the driven part is a toothed pulley (4) on a driven side, and the tension-bearing belt (2) is engaged with a toothed belt (2) engaged with the toothed pulley (4) on the driven side. Belt transmission method characterized in that 1) is coated in a frictional force transmission state. The belt transmission method according to claim 1 or 2, wherein the tensile force of the tension-bearing belt (1) is a steel belt of about 15 kgf / mm to 25 kgf / mm per unit width. An electric transmission comprising a toothed belt 2 engaged with a toothed pulley 4 and a tension-bearing belt 1 having a large tensile force coated on the toothed belt 2 in a frictional force transmission state. belt. The toothed belt (2) according to claim 4, wherein the toothed belt (2) is provided with a looped toothed belt (20) which is provided between the toothed pulley (4) on the driving side and the toothed pulley (4) on the driven side. 2), wherein the tension-bearing belt (1) is a loop shape covered with the loop-shaped toothed belt (2). 5. The transmission belt according to claim 4, wherein the toothed belt (2) is provided only at an engagement portion with the toothed pulley (4) as a transmission belt for transmitting a reciprocating movement of a predetermined length. The belt according to claim 4 or 5, wherein the tension-bearing belt (1) is a steel belt having a tensile strength of about 15 kgf / mm to 25 kgf / mm per unit width. 8. The transmission belt according to claim 7, wherein the tension bearing belt (1) is a steel belt having a thickness of about 0.15 mm to 0.25 mm. The transmission belt according to any one of claims 4 to 8, wherein the tension burden belt (1) is formed with a plurality of holes continuously formed at a predetermined pitch. 10. The transmission belt according to claim 9, wherein each of the holes is a burring hole protruding toward the toothed belt (2). The tension-bearing belt (1) according to any one of claims 4 to 10, wherein the tension-bearing belt (1) has a narrower band shape than that of the toothed belt (2), and the surface of the toothed belt (2) is described above. Transmission belt characterized in that the convex group 29 is formed along both edges of the tension-bearing belt (1). 12. The transmission belt according to any one of claims 4 to 11, wherein the surface of the tension-bearing belt (1) is covered by a coating layer integrated with the toothed belt (2). In the belt transmission apparatus wherein the toothed pulley (4) on the drive side and the toothed pulley (4) on the driven side are driven by a toothed belt (2) meshing with them, the pair of toothed types Between the pulleys 4, the idler rollers 3 external to the toothed belt 2 are freely provided with external force control, and the toothed belts meshing with the toothed pulleys 4 ( A tension-bearing belt 1 is provided on the outer circumferential surface of 2) in a frictional force transmission state, and the idle roller (inside the running portion of the tension-bearing belt 1 between the toothed pulleys 4). Belt transmission device characterized in that 3) is installed. 15. The toothed belt (2) according to claim 13, wherein the end of the toothed belt (2) is fixed in engagement with one of the toothed pulleys (4), and the end of the tension-bearing belt (1) has a toothed tooth. A belt transmission device characterized in that it is fixed to the end of the toothed belt (2) engaging the attachment pulley (4) in an external state. 15. The belt transmission apparatus according to claim 13 or 14, wherein the tension of the tension-bearing belt (1) is a steel belt of about 15 kgf / mm to 25 kgf / mm per unit width. The method according to any one of claims 13 to 15, wherein the idle roller (3) is provided between the running area of the toothed belt (2) and the running area of the tension-bearing belt (1), respectively. The belt transmission device characterized by the belt which made the said external force free to adjust by mutually separating these idle rollers (3) mutually. The apparatus according to claim 13, wherein the swing arm on the driven side is freely rotatably supported at the tip of the arm swinging to the reciprocating point shaft and swinging in accordance with the rotation of the point shaft. The toothed pulley 4 on the drive side is fixed to the supporting portion of the point shaft, and the driven toothed pulley 4 is attached to the rotating shaft portion of the rocking arm on the driven side. Powertrain.