JPWO2008105345A1 - Transmission device and transmission body - Google Patents

Abstract

The present invention relates to a closed-loop-shaped transmission body that spans between a plurality of direction change imparting means (for example, pulleys) for transmission, and smooth rotation is performed in a path in contact with the direction change imparting means. It is an object of the present invention to provide a transmission body that forms a possible first sector and forms a second sector of a rigid structure along an arc path in a path between direction change imparting means, and a transmission device using the transmission body. SOLUTION: A plurality of direction change giving means (P) and a direction change giving means (P) are composed of a closed loop-shaped transmission body (B) bridged between the direction change giving means (P), and the transmission body (B) is turned around ( R1) and the direction change imparting means path (R2), the turning path (R1) is formed in the first arc (A1) centered on the center of each direction change imparting means (P). The path (R2) between the direction change imparting means is formed in the second arc (A2) between the direction change imparting means (P) and (P), so that the entire path along which the transmission body (B) travels is formed. A transmission device characterized by being formed into an arc. [Selection] Figure 1

Description

<Technical field to which the invention belongs>
INDUSTRIAL APPLICABILITY The present invention is a transmission device comprising a plurality of direction change imparting means (for example, pulleys) and a closed loop-shaped transmission member spanned between the direction change imparting means, and particularly used in various fields including the automobile field. The present invention relates to a continuously variable transmission (CVT) using a closed loop transmission body.
Further, the present invention provides a transmission body that spans between a plurality of direction change imparting means (for example, pulleys), in particular, a closed loop transmission body for a continuously variable transmission used in various fields including the automobile field, It is about.

<Conventional technology>
[Transmission body, especially belt body]
Generally as a transmission body used for the transmission apparatus of the mechanism which repeats rotation or reciprocation in one direction, a ring body and a tension type belt body are used. Among these, a general-purpose tension belt body is stretched over a direction change imparting means generally composed of a rotating body such as a pulley or a roller, and transmission is performed by the belt body traveling between the direction change imparting means. Depending on the application, a fixed structure that does not rotate may be used as the direction change imparting means.

  For example, when a pulley is used as the direction change imparting means, such a path of the transmission body includes a path that is in contact with the pulley and a path between the pulleys that is not in contact with the pulley. When the transmission body is a tension belt, transmission is performed by a tension difference generated between the forward path and the return path in the path between pulleys.

  In the transmission system using such a tension difference, various explanations are made in various manuals on the assumption that the path not in contact with the pulley is constituted by a linear structure (for example, Non-Patent Document 1 “Practical design of new version belt transmission and precision conveyance, editor: belt transmission technology social gathering, issue place: Yokendo, issue date: August 19, 2006, first edition issue”). There are many documents expressing the path portion between the pulleys on which the belt body travels in terms of “straight line portion” or “string portion”.

[CVTs of various types]
As a continuously variable transmission (CVT) mounted on automobiles, in addition to the belt-type CVT (belt-CVT) using the tension-type belt having the above characteristics, a full-toroidal traction-CVT ), Various types such as a traction drive type CVT such as a half-toroidal traction-CVT have been developed.
At present, the belt type CVT is most widely distributed mainly in the field for low torque vehicles.

  The belt system CVT typically has a closed-loop V-belt stretched between pulleys having V-shaped grooves each having two sheaves, one of which is variable. Here, the V-belt is a belt in which a portion of the pulley that contacts the V-shaped groove has a tapered cross section.

  Note that a mono-ring type CVT has been studied as being included in the category of the traction drive type CVT. That is, Japanese Patent Application Laid-Open No. 2004-263857 (Patent Document 16) proposes a method using a ring whose outer peripheral side is formed in a gear shape. The mono ring type CVT will be described in more detail later.

  Non-Patent Document 2 (“Introduction to CVT, Author: Yoshiro Morimoto, Publisher: Grand Prix Publishing Co., Ltd., Issued: First edition published on October 25, 2004”), including belt-type CVT Detailed explanation about CVT in general is made, so that the whole picture of CVT can be known.

[Various types of belt type CVT]
There are several types of V-belts used in the belt system CVT. Examples of belts that have been put into practical use in the past, belts that have been put into practical use, or belts that are thought to have influenced current practical use include the following.
V1: Rubber V-belt V2: Multi-layer hoop type V-belt (that is, a V-belt in which metal hoops are nested in multiple layers)
V3: Multi-layer hoop-element combination type V belt (that is, a V-belt having a structure in which a large number of elements are fitted over the entire circumference of a multi-layer hoop in which metal hoops are nested and non-fixed in multiple layers)
V4: Chain-type V-belt V5: Composite V-belt (V-belt with a structure in which a heat-resistant resin block with metal plate reinforcement is sandwiched between rubber belts with core wires)

[V1: Rubber V-belt]
The rubber V-belt is a rubber belt containing a core material whose both side surfaces are inclined surfaces.
When this rubber V-belt is used, both side surfaces of the belt are in direct contact with the inclined surface of the V-shaped groove of the pulley, and torque is transmitted between the belt and the pulley. The tensile force of the belt is enhanced by the core material.

[V2: Multi-layer hoop type V belt]
The multi-layer hoop type V-belt uses a hoop (annular band) produced by welding the beginning and end of a strip-shaped metal thin plate, and produces hoops with slightly different circumferences and slightly different widths. The hoop is a V-belt in which the hoops are stacked in multiple layers in a non-fixed state so that both side surfaces are inclined. In this belt, both side surfaces of the multilayer hoop directly contact the inclined surface of the V-shaped groove of the pulley, and torque is transmitted between the belt and the pulley. The belt tension is borne by the individual hoops.

  A typical example of this multi-layer hoop type V-belt is US Pat. No. 3,604,283 (patent document 1) whose priority date is 1968, and is a direct predecessor of “V3: multi-layer hoop-element type V belt” described below. It seems to be a technology.

[V3: Multi-layer hoop-element combination type V belt]
Multi-layer hoop-element combination V belt is a multi-layer metal hoop according to the above (however, each hoop has a slightly different circumference but the width is the same) and a number of elements with both side surfaces being V-shaped inclined surfaces (Block) and a belt.
In this V-belt, the multilayer metal hoop does not contact the inclined surface of the V-shaped groove of the pulley, and both side surfaces of the element contact the inclined surface of the V-shaped groove of the pulley. The torque is transmitted through the element.

As described above, when a belt is stretched between two pulleys and operated to transmit force and torque, a tension-side path and a slack-side path are generated.
Even in the above-described multi-layer hoop-element combined type V belt, the tension of the belt is borne by each hoop. Therefore, from the viewpoint of the tensile force alone, when transmitting force and torque, the tension side path and the loose side Should result in the following path.

  However, in the multi-layer hoop-element combined type V belt, the following phenomenon occurs when driven by applying a load to the driven pulley side. That is, only the tensile force is working in the tight path. As for the slack side path, the elements are in a compressed state just before exiting the drive pulley, and just before the driven pulley is turned around via the slack side path. It seems that the pressing force by the element works complementarily.

  Therefore, this multi-layer hoop-element combination V belt is generally called a "compression type" belt (a belt of a type that transmits power by compression between elements), but the main role is only a tensile force, and it is loose In the side path, it can be said that the belt is supplemented by the compressive force of the element. Non-Patent Document 3 (“Kanehara, Kitagawa, Kurokawa, Fujii:“ Distribution of inter-block pushing force and ring tension of CVT metal belt ”, Vol. 25, No. 4, October 1994, p. 125-130 "), see page 3.3, page 130.

  US Pat. No. 3,720,113 (patent document 2) related to the application in 1971 is this multilayer hoop-element combination type V-belt. A large number of applications have been filed for improvement.

  This type of V-belt can be said to be a typical belt type CVT for automobiles that automobile manufacturers currently employ in many (rather than most) vehicle types.

(Improved invention of V3 belt)
Regarding the V3 belt, applications for improvement such as the following (i), (ii), and (iii) have been filed. (i) is related to a device for eliminating a gap between elements, and (ii) and (iii) are related to a device for making the compression state between elements more reliable.
In the following three publications, among the reciprocating paths between the pulleys, a path in which the force is applied in the direction in which the tensile force of the multi-layer hoop is loosened (the element is compressed) in a state where a load is applied to the V-belt is referred to as a “loosening side path. The path in which the force is applied in the direction in which the tensile force of the multi-layer hoop increases (the element is not compressed) is expressed as the “stretch side path”.

  (i) International Publication WO02 / 053939 (Special Table 2004-517274) (Patent Document 13) describes that the thickness of the upper side of the element is made larger than the thickness of the lower side to form an arc. Has been. In FIG. 7, the slack side path (upper path in the figure) is drawn with a solid convex arc, and the tight path (lower path in the figure) is a solid concave arc (element travel path). And a dashed-dotted straight line (traveling path of the multi-layer hoop). The path formed by the hoop and the path formed by the element row are deviated.

  Incidentally, the same applicant's international publication wo02 / 053935, international publication wo02 / 053936 (special table 2004-517273) publication, international publication wo02 / 053937 publication, international publication wo02 / 053938 publication, international publication wo02 / 053939 by the same applicant. The same belt path (both in FIG. 7) is also drawn in (Tokuyo 2004-517274) and European Publication 121860 (Japanese Patent Laid-Open No. 2002-227936).

(ii) JP 2001-59551 A (Patent Document 14)
“A combination of a metal ring assembly in which a plurality of endless metal rings are laminated and a number of metal elements having ring slots into which the metal ring assembly is fitted, and both pulleys are wound around a drive pulley and a driven pulley. In the belt for continuously variable transmission that transmits the driving force between
The radial position of the geometric center of the three contact surfaces that transmit the compressive load in the front-rear direction to a part of the main surface of the metal element, the center in the thickness direction of the metal ring assembly fitted in the ring slot, and the ring A belt for a continuously variable transmission, characterized in that it is set between the outer peripheral edge of the slot in the radial direction. "
Is described.
In FIG. 8B, a slack side path in which the compression side string part is warped and a tension side path in which the opposite side of the compression string part is a straight line are drawn. A slack side path in which the part is warped and a tension side path in which the opposite side of the compression side chord part is straight are drawn. (The chord is the path between pulleys.)
In this publication (ii), “FIG. 8 (A) shows an ideal state in which the chord portion on the compression side has a linear shape. In this state, the pressing force between the metal elements is most effective. In addition, the load applied to the inner peripheral surface of the metal ring assembly from the saddle surface of the ring slot of the metal element is reduced, and the fatigue life of the metal ring assembly is extended. "(Paragraph 0002, 5 to 11 lines from the top). In addition, the tension side chord part becomes a straight line in principle, and this tension side chord part cannot be warped or inwardly warped.

  (iii) Japanese Patent Application Laid-Open No. 2002-213539 (Patent Document 15) describes an element for a CVT belt having a structure similar to the metal element of (ii) above, “the mutual contact reference surface formed on the ear part, If there is a difference in plate thickness between the neck part and the mutual contact reference surface formed on the part close to the saddle part, the neck part flank equivalent part will bend and deform to cause mutual deformation on the ear part side. It works to absorb the difference in plate thickness between the contact reference surface and the mutual reference surface on the neck side, so that the belt straight part is not necessarily a perfect straight line but a relatively large arc. However, since the elements forming the CVT belt are in a form in which at least three mutual contact reference surfaces are in intimate contact with each other, the running stability of the CVT belt is good. Paragraph number 0011, 8 lines from the top to the bottom line).

  In FIG. 4, both the upper and lower paths are drawn as a convex arc and a ladder-like straight line (two parallel straight lines and almost equally spaced partition lines represent the element alignment state). However, this only draws two cases on one drawing: a case where the upper path is convex and a case where the lower path is convex.

Since the CVT belt using the CVT belt element of this publication has the same arc structure as the continuously variable transmission belt of (ii) above, it is clear that the tension side path is a straight line.
FIG. 4 of this publication is a diagram showing that when a load is applied, the upper and lower paths can travel with a convex arc (the element is in a compressed state), and two paths, a loose side path and a tension side path, are shown. Indicates a set of routes on which the CVT belt travels.

[V4: Chain type V belt]
Chain type V-belts have also been proposed for a long time.
In general, a chain is composed mainly of a plate and a pin. For a chain-type belt, depending on which part of the chain is brought into contact with the V-shaped groove of the pulley, for example, the following mechanism is used. There is. (Note that, in any chain belt, both of the reciprocating paths are straight lines.)

V4a: A method in which the plate portion of the chain is brought into contact with the V-shaped groove of the pulley (that is, a structure in which the convex portion provided on the side surface of the plate, which is a component of the chain, is brought into contact with the pulley)
An example of this type of chain V-belt is U.S. Pat. No. 9,595,532 (patent document 3) filed in 1908.

V4b: A system in which the plate of the chain itself is provided with irregularities, and the convex part is brought into contact with the V-shaped groove of the pulley. This type of chain-type V-belt includes, for example, Japanese Patent Application Laid-Open No. 2004-197948 whose priority date is 2002 (Patent Document 4).

V4c: A system in which a member attached to an opening provided in a plate of a chain is brought into contact with a V-shaped groove of a pulley (that is, a bundle of a plurality of thin plates inserted into an opening provided in a plate which is a constituent member of a chain Structure to contact)
An example of this type of chain-type V-belt is U.S. Pat. No. 20,385,583 (patent document 5) having a US filing date of 1934.

V4d: A system in which a member provided surrounding a plate of a chain is brought into contact with a V-shaped groove of the pulley (that is, a frame-like member is provided so as to surround a plate which is a constituent member of the chain, and the member is brought into contact with the pulley)
An example of this type of chain type V-belt is US Pat. No. 4,392,843 (patent document 6) filed in 1980.

V4e: A system in which both end surfaces of a pin of a chain are brought into contact with a V-shaped groove of a pulley. For example, US Pat. No. 6,293,887 (Patent Document 7) has a priority date of 1999.

V4f: A system in which a block provided at the lower part of the chain (inner side of the belt) is brought into contact with the V-shaped groove of the pulley. This type of chain type V-belt is disclosed in, for example, Japanese Patent Application Laid-Open No. 9-42383, filed in 1995. There is a publication (Patent Document 8).

V4g: A system in which a block having an internal chain structure is brought into contact with a V-shaped groove of a pulley. For this type of chain-type V-belt, for example, Japanese Patent Laid-Open No. 6-185578 (Patent Document 9) filed in 1983 is disclosed. is there.

[V5: Composite V belt]
The composite V-belt is a belt having a structure in which a heat-resistant resin block with a reinforcing metal plate is sandwiched between rubber belt tension bands containing core wires.
This type of composite V-belt is considered to have been improved for practical use based on Japanese Patent Application Laid-Open No. 60-49151 (Patent Document 10) filed in 1983. In this composite belt, the rubber belt tension band is responsible for the tensile force. The force is transmitted mainly by “pulley → block → rubber belt tension band”, but since the rubber belt tension band also contacts the pulley, a part of the force is transmitted as “pulley → rubber belt tension band”.

  A composite belt similar to the above is also shown in Japanese Patent Application Laid-Open No. 11-280849 (Patent Document 11), which was filed in 1998. The member corresponding to the block consists of an arch-shaped upper beam part and a downwardly extending pillar (two side pillars and one center pillar), and the contact part between the block side face and the pulley is the tension of the rubber belt containing the core wire in the drawing. It seems to be the upper half side of the center belt corresponding to the belt. (Note that the arch-shaped upper beam portion is the shape of the block as viewed from the front where the both sides of the upper beam portion are chamfered.)

[Belt system CVT from the viewpoint of force and torque transmission system]
When a closed-loop V-belt is stretched between the pulleys, torque is transmitted between the pulley and the belt in a “pulley turning path” in which the belt turns the pulley. In order to transmit torque at this time, frictional force based on the clamping force generated between the belt and the pulley is used. For that purpose, the pulley pressing force (clamping force) against the belt is set to a predetermined value. This should be set to prevent the belt from slipping.

On the other hand, in the “path between pulleys” between the pulleys, the force is transmitted by the belt. And in the transmission system of force in the path between pulleys,
1. A method that uses only the belt tension difference that occurs in the reciprocating path between pulleys ("tensile belt"),
2. In one of the reciprocating paths between the pulleys as in “V3: multi-layer hoop-element combined type V belt” described above (more precisely, it is driven through a path on the loose side slightly before leaving the driving pulley. A method that uses the compressive force of the elements complementarily while making the hoop exert a tensile force (in the stage just before the pulley is turned), and uses only the tensile force of the belt in the other path (so-called “compression” Expression belt ")
There are two methods.

The following table 1 summarizes the force transmission systems that are effectively used in the five types of belt systems CVT described above.
V3 multi-layer hoop-element combination V-belts are often described as "compression belts", but they are compressed in one of the reciprocating paths and the multi-layer hoops that carry the tensile force in the reciprocating paths. The elements that contribute to the transmission in a complementary manner by exerting the force play their respective roles, so the “tensile belt using the compression force in a complementary manner” is more accurate.

<Problems of conventional technology>
[Limitation of mono ring CVT]
The monoring system CVT disclosed in Japanese Patent Laid-Open No. 2004-263857 (Patent Document 16) described in the section of [Various types of CVT] is a pulley having a V-shaped groove and a single toothed belt having a tapered side surface. It is noteworthy in that a rigid ring is used as a transmission body instead of a flexible V-belt.
However, this mono-ring type CVT, like the various traction drive systems, has a structure that allows the ring itself to withstand a large pressure contact despite the fact that torque is transmitted by one-point contact between the ring and the driving pulley. There is a problem that it is difficult to make it difficult, and there is a problem that efficiency and power transmission tend to be halfway. This mono-ring CVT is considered suitable for automobiles with a small displacement.

[Common problems with being a tension belt]
In the five types of belt type CVTs V1 to V5 described in the section of the prior art, including those already widely used such as the V3 type belt type CVT, as described below. Includes limitations, problems, or solutions.

-1-
The biggest and essential problem is that it can be said in common for any of the V1 to V5 V belts including V3, but the force transmission method in these belts uses a tensile force. This is a problem caused by the problem.

-2-
That is, in the tension type belt, in consideration of the fact that the tension applied to the belt increases as the load on the driven shaft increases, a tension resistant part that can withstand the tension when the load is large must be used. .
In order to produce a belt having high tensile strength that can be used for automobiles (especially for automobiles with a large displacement) while ensuring the flexibility with which the pulley can be rotated, the material of the belt and the belt It is inevitable that the structure is constrained, the belt becomes larger and the weight increases. These problems are directly connected to an increase in the manufacturing cost of the belt and a disadvantage in fuel consumption due to an increase in weight of the CVT on which the belt is mounted.

  Moreover, even if a belt with a sufficient tensile force is used in the initial stage, the belt circumference will gradually increase with the passage of the service period because it is used under conditions close to the limit of its tensile strength. I can not escape. To absorb belt elongation, increase the hydraulic pressure applied to the pulley to reduce the width of the V-shaped groove (that is, stretch the belt on the outer periphery of the pulley) and the distance between the pulleys (distance between the shafts) However, even if such an adjustment is made, the belt will be stretched again, and in some cases it may not be possible to adjust only (the limit of adjustment may be reached).

-3-
For example, in the case of a tension belt used for automobiles, a large tensile force is applied to the belt at the pulley inlet on the drive side (with a small diameter) when the gear ratio is other than 1: 1 and a load is applied. At the same time, the radius of engagement with the pulley tends to be reduced, while the pulley entrance on the driven side (with a large diameter) is on the loose side, so a small pulling force is likely to increase the engagement radius of the belt with the pulley. As a result, it is inevitable that the force to try to shift to the low side will work. Note that the reverse operation occurs during reverse driving, such as during engine braking. (Refer to the description of FIG. 3-21 on page 58 and FIG. 5-4 on pages 126 to 127 and FIG. 5-5 in the previous Non-Patent Document 2 (Introduction to CVT).)

  As for this problem, when controlling the hydraulic pressure for each pulley, it is necessary to adjust the pressing force (clamping force) by adopting a control program that takes into account items that cancel the shifting tendency toward the low side. In addition to the complexity of the program, the clamping force is excessive and tends to be energetically disadvantageous.

  In addition, in the tension belt, the movable sheave of the pulley has a strong force in the opposite direction to the fixed sheave, so the parallelism between the sheaves is lost and the pulley tends to be deformed. It also places a heavy burden on the shaft. Therefore, the pulley (and its shaft) must be designed robustly, and there is little room for its compactness and weight reduction. (See the description on pages 40-44 of the previous Non-Patent Document 2 (Introduction to CVT) and FIGS. 3-7 and 3-9.)

[Individual problems with belts V1 to V5]
Next, the problems of the belts V1 to V5 will be individually examined.

[V1: Rubber V-belt]
The V1 rubber V-belt has the problems caused by the tension type described above as well as its torque and force transmission, and its durability and heat resistance are also limited. . For this reason, although it has been put into practical use as a CVT belt for two-wheeled vehicles, there is a track record of studying a CVT belt for automobiles, but it is not easy to put into practical use.

[V2: Multi-layer hoop type V belt]
The V2 multilayer hoop type V-belt is not easy to produce a hoop by welding the start and end of a strip-shaped metal thin plate, and the circumference of the hoop is slightly different and the width is also slightly different. It is not easy to manufacture a product accurately, it is not easy to inspect the product belt, and there is a disadvantage that the manufacturing cost is high. Further, even if these problems are overcome by improvement of manufacturing technology, the essential problems caused by the tension belt described above are not overcome.
However, it is considered that the historical significance that this V2 multi-layer hoop type V-belt produced the V3 multi-layer hoop-element type V-belt is great.

[V3: Multi-layer hoop-element combination type V belt]
V3 multi-layer hoop-element combination type V-belt is a combination of multi-layer hoops and elements that play the role of torque transmission between the pulley and the belt, and the element has a reciprocating path between the belt pulleys. In one of the paths (more precisely, a little before exiting the drive pulley and a little before completing the rotation of the driven pulley via the loose side path) It can be said that it is original in the tension type V-belt in that it plays a role.

However, even in this V3 belt, the compression force exerted together with the tensile force is limited to only one of the reciprocating paths between the pulleys of the belt (the other path exhibits only the tensile force). ), The compressive force is expressed only in the state where the tension remains on the loose side, and the essential problems caused by the tension type belt described above cannot be sufficiently solved.
It is difficult to solve the problem described in -3- of [Problem common to being a tension belt] even with the belt of V3.

  In addition, the V3 belt is not easy to meet the accuracy required for the manufacture of the hoop and the element, and thus there is a limit to the reduction of the defective rate and the cost reduction. In other words, it is required to accurately manufacture hoops with slightly different perimeters, and for the elements on the front and back surfaces, contact portions with adjacent elements (element width x height of about 1 mm). Where high precision parallelism is required, both the hoop and the element have a high rate of being out of specification in the final inspection process.

In addition, with this V3 belt,
・ Since the multi-layer hoop and the element have their own functions and movements, the multi-layer hoop and the element do not synchronize with each other. To become a,
-In the path where the belt rolls around the pulley, the elements do not line up neatly (for example, the contact point of the front and rear elements that cause the elements to become rod-shaped differs from the contact point of the front and rear elements due to congestion during pulley rotation. Because of this, the posture of the element when viewed from the center of the pulley tends to lean forward or backward)
-Deviation between the hoops constituting the multi-layer hoop (the number of layers is often around 10 layers) (displacement always occurs when traveling one round, and the deviation at that time is as much as the outer hoop). large),
・ Since the innermost layer of the multi-layer hoops is most stressed, the innermost layer hoops are most susceptible to damage,
Therefore, there are limitations in terms of energy loss and belt life.

For example, from the viewpoint of energy loss, the CVT (continuously variable transmission) using the V3 belt uses a gear type automatic transmission (AT) while having the advantage of CVT. There is a disadvantage that there is no advantage in terms of fuel consumption especially in high-speed driving compared to the case where there is.
In addition, the V3 belt has a problem in that the weight and size of the belt must be increased in order to withstand the mounting on a vehicle having a large displacement, and it is not easy to make it compact and lightweight.

  In addition, the V3 belt has a problem that it is not easy to fit the elements around the multilayer hoop when assembling the belt, and the elements cannot be fitted exactly around the multilayer hoop. There is also a problem that it is not possible to prevent gaps between elements.

(Improved invention of V3 belt)
(i) Japanese Patent Application Publication No. 2004-517274 (Patent Document 13) describes that the problem to be solved is “to eliminate a gap between elements”. In order to achieve this task, due to dimensional constraints in the manufacture of the V-belt, (a) a method in which the total thickness of the elements is the same as the length of the entire circumference of the multilayer hoop, and (b) The method of making it larger than the circumference must be adopted.

Of these dimensional constraints, (a) is a method that cannot be realized in view of manufacturing errors, so (b) is a reasonable method.
In other words, the V-belt of this publication (i) naturally has the total thickness of the elements larger than the length of the entire circumference of the multilayer hoop. It must be a convex arc on the inner peripheral side of the. In fact, in FIG. 7, the layered hoop path is drawn with a one-dot chain line in the tension side path (lower path in the figure), and the element path is drawn with a solid arc (the element row and the hoop are separated). You know).
Therefore, since the V belt of this publication is a belt in which the tensile force of the multilayer hoop increases when a load is applied, the problems of the V3 V belt cannot be solved sufficiently.

(ii) In Japanese Patent Laid-Open No. 2001-59551 (Patent Document 14), the tension side path (the lower path in the figure) is drawn with a straight line in FIGS. 8 (A), (B), and (C). From this, the V-belt of this publication is (i)
As in the case of the belt, the tensile force applied to the multilayer hoop increases when a load is applied, and the problem of the V3 V belt cannot be solved sufficiently.

  (iii) The V belt disclosed in Japanese Patent Laid-Open No. 2002-213539 (Patent Document 15) also has basically the same structure as the V belt described in (ii) above, as described in the section of <Conventional Technology> As in the case of the belt, the tensile force applied to the multilayer hoop increases when a load is applied, and the problem of the V3 V belt cannot be solved sufficiently.

[V4: Chain type V belt]
Even with the V4 chain-type V-belt, the essential problems caused by the tension-type belt described above cannot be overcome.
In addition, it is a chain type that consists mainly of plates and pins, and it is difficult to reduce the weight and size of the plates and pins to be used because it is difficult to reduce the weight and size of the plates and pins used. This leads to the disadvantage that noise reduction is not easy.

[V5: Composite V belt]
The V5 composite V-belt also has some advantages over other systems, but it does not overcome the essential problems caused by the tension-type belt described above, and the heat resistance by using rubber. There is a problem of durability, and there is a question about durability. Therefore, it seems that there is a limit that it can not be used as a V-belt for a belt type CVT to be mounted on an automobile with a large displacement even when applied to an automobile with a small displacement such as a light vehicle.

"Practical design of belt transmission and precision conveyance", edited by: Belt transmission technology social gathering, publisher: Yokendo, issue date: August 19, 2006 "Introduction to continuously variable transmission CVT", author: Yoshiro Morimoto, publisher: Grand Prix Publishing Co., Ltd., published: October 25, 2004 “Kanehara, Kitagawa, Kurokawa, Fujii:“ Distribution of inter-block pushing force and ring tension of metal belt for CVT ”, Automobile Engineering Association Proceedings, Vol. 25, No. 4, October 1994, p.125-130 US Pat. No. 3,604,283 U.S. Pat. No. 3,720,113 U.S. Patent No. 959532 JP 2004-197948 US 2038583 U.S. Pat. No. 4,392,843 US Pat. No. 6,293,887 Japanese Patent Laid-Open No. 9-42383 JP-A-6-185578 JP-A-60-49151 Japanese Patent Laid-Open No. 11-280849 International Publication WO02 / 053939 JP 2001-59551 A JP 2002-213539 A JP 2004-263857 A

[Object of invention]
An object of the present invention is to provide a transmission body that is fundamentally different in principle and mechanism as compared with a conventional transmission body, and that is remarkably superior in terms of operational effects. More specifically, it is a closed loop-shaped transmission body that spans between a plurality of direction change imparting means (for example, pulleys) for transmission, and can smoothly turn in a path that contacts the direction change imparting means. An object of the present invention is to provide a transmission body that forms a first sector while forming a second sector of a rigid structure along the arc path in the path between the direction change imparting means.
Another object of the present invention is to provide a transmission device using such a transmission body, in particular, to provide a continuously variable transmission (CVT).

[Transmission device of the present invention]
The transmission device of the present invention is
It consists of a plurality of direction change giving means (P) and a direction change giving means (P).
The transmission body (B) is a closed loop comprising a turning path (R1) for turning each direction change giving means (P), and a direction change giving means (P)... In a transmission that travels on a route,
(X) The turning path (R1) is formed in a first arc (A1) that protrudes from the center of the turning path (R1) to the outer peripheral side of the transmission body (B),
(Y) The direction change imparting means paths (R2) are convex on the outer peripheral side of the transmission body (B) in all the direction change assignment means paths (R2) or all the direction change assignment means paths In (R2), a second arc (A2) is formed that protrudes toward the inner periphery of the transmission body (B).
Therefore, the entire path traveled by the transmission body (B) is formed in an arc,
It is characterized by.

<Transmission body of the present invention>
The transmission body of the present invention is
A plurality of direction change granting means (P)... A turn path (R1) that turns each direction change granting means (P) by passing between them, and a direction change granting means (P). A closed loop transmission body (B) for traveling along the intermediate path (R2),
In the transmission body (B), a large number of swirlers (1) are restrained by the restraining means (2) at the restraining portion (S), and the swirler (1) and the restraining means (2) are all synchronized. Comprising an array arranged in a closed loop traveling along a route, and
Individual swirlers (1) restrained in the restraint (S)
(M) It is configured to be swingable around the restraining portion (S), and
(N) When the swirler (1) is pressed against each other so that their dorsal abdomen (1b) and (1b) face each other, a convex arc is formed on the outer peripheral side or inner peripheral side of the transmission body (B). The pressure contact assembly (1n) has a shape or structure that is autonomously formed,
In a state where the transmission body (B) is bridged between the direction change grant means (P).
(X) The turning path (R1) is transmitted to the center of the center of the turning path (R1) by the unfolding of the swirler (1). B) is formed on the first arc (A1) that protrudes to the outer peripheral side,
(Y) The path (R2) between the direction change imparting means is overlapped so that the swirlers (1) which are restrained in the restraining part (S) are in contact with each other between the dorsal abdominal parts (1b) and (1b). (Folded), a convex arc is formed on the outer peripheral side of the transmission body (B) in all the paths (R2) between the direction change giving means, or the transmission bodies in all the direction change giving means paths (R2) (B) The second arc that hangs between adjacent direction-changing imparting means (P) and (P) by autonomously forming a press-contact assembly (1n) structure that forms a convex arc on the inner circumference side of (B) Formed in (A2),
Therefore, the entire path traveled by the transmission body (B) is formed in an arc,
As a result, the array forms a first sector having the same curvature as the first arc (A1) in the turning path (R1), and in the path (R2) between the direction change imparting means. Forming a second sector having the same curvature as two arcs (A2);
It is characterized by.

<Detailed Description of the Invention>
Hereinafter, the present invention will be described in detail.

[Transmission device]
[Driving path of transmission body (B) in transmission device]
The transmission device of the present invention comprises a plurality of direction change imparting means (P), and a direction change imparting means (P). This transmission body (B) forms a turn path (R1) for turning each direction change imparting means (P) and a direction change grant means (P)... Drive to.

[Direction change grant means (P)]
Examples of the direction change imparting means (P) include a structure in which the direction change imparting means (P) itself can rotate, such as a gear, a roller, and a pulley, and the pulley is particularly important.
When the outer surface of the transmission body (B) is used for the purpose of, for example, pressure bonding, the direction change providing means (P) itself may be a fixed object that does not rotate.
The direction change imparting means (P) may be provided with an additional means using a heating device, a cooling device, a blower device, a pressurizing device, or the like, if necessary.
The direction change providing means (P) may be, for example, a transmission body (B) sandwiched between pulleys as long as it satisfies the functions required as a transmission device.

When the direction change imparting means (P) is a gear, the inner peripheral side and / or side surface of the transmission body (B) can be used as a contact portion for transmission with the gear. Further, it is possible to provide the transmission body (B) with an engaging portion corresponding to the tooth profile of the gear so that the engaging portion and the gear mesh with each other.
Examples of such gears include spur gears, helical gears, helical gears, and bevel gears. The tooth profile of the gear may be a commonly used shape such as an involute tooth profile, but it is a special shape not described in the JIS standards, etc., considering the meshing with the contact part of the transmission body (B). Also good. Similar to the tooth profile, the number of teeth may be a standard product or a number other than the standard product.
The gears can be used alone as the direction changing means (P), or a plurality of them can be used as the direction changing means (P).

When the direction change providing means (P) is a roller, for example, the inner peripheral side or / and the side surface of the transmission body (B) can be used as a contact portion for transmission with the roller.
Examples of the shape of such a roller include a columnar shape, a truncated cone shape, and a conical shape. In some cases, the cross-sectional shape may be an ellipse or a polygon.
The rollers can be used alone as the direction change imparting means (P), but a plurality of them can be used as a direction change means (P).

When the direction change imparting means (P) is a pulley, for example, the inner peripheral surface and / or side surface of the transmission body (B) can be used as a contact portion for transmission with the pulley.
Various types of pulleys such as those having V-shaped grooves are used as such pulleys, but when the transmission is a continuously variable transmission (CVT), at least one of the two pulleys is in a variable state. A pulley having a V-shaped groove using a sheave is preferably used. Below, the case where the pulley which has such a variable V-shaped groove is used is demonstrated.

A typical example of a pulley having a variable V-shaped groove is a fixed sheave (Pfs) and a movable sheave (Pms) arranged so that their cone surfaces (conical surfaces) face each other, as shown in FIG. It is a thing. If the inclination angle (sheave angle) of the cone surface of each sheave is α, the angle of the V-shaped groove of the pulley is 2α.
There are various types of pulleys having V-shaped grooves.

For continuously variable transmission,
-A system in which the distance between the shafts between the pulleys is constant, and the width of the V-shaped groove of both the driving side and driven side pulleys is variable.
・ A system in which the distance between the shafts between the pulleys is variable, and the width of the V-shaped groove of one or both of the driving side and driven side pulleys is variable,
However, in the case of a continuously variable transmission for automobiles, for example, the former constant axis distance method is often adopted.

The sheave angle α described above is the material of the pulley, the surface condition of the pulley, the material of the swivel (1), the surface condition of both sides of the swivel (1), the swivel (1)-the restraining means (2) The optimum value should be selected by comprehensively considering the engagement mechanism between them and the use of oil for reducing friction between the pulley and the transmission body (B).
When the coefficient of friction between the pulley and the transmission body (B) is, for example, 0.08 to 0.2 or around that due to the use of oil, the sheave angle α is often about 11 ° (for example, 11 ° ± 3 °).
When oil is not used, the coefficient of friction increases, so the sheave angle α may be set to about 13 ° (for example, 13 ° ± 2 °).

  Note that the sheave angle α of the pulley is often set as described above, but the sheave (fixed sheave (Pfs) and mobile The cone surface of the sheave (Pms) can be formed into a curved surface that is slightly convex, or can be formed into a curved surface that gradually changes the inclination angle.

  Usually, the number of direction change providing means (P) is two, but it can be three or more. Below, the case where a transmission body (B) is bridged between two direction change provision means (P) and (P) is mainly demonstrated.

[Transmission body (B)]
The transmission body (B) of the present invention includes a method of utilizing the gravity of the transmission body (B) itself, a method of increasing the inter-axis distance between the direction change imparting means (P), and the direction change imparting means (P). By changing the gap, pressing the transmission body (B) between the direction change imparting means (P) with a roller, or combining these methods, the direction change imparting means (P)... The second sector can be a rigid structure.
The second sector of the rigid structure can be used as a means for transmitting power from one direction change imparting means (P) to the other direction change means (P). Further, it can also be used as means for transmitting power to other than the direction change providing means (P) by bringing the outer peripheral side upper surface of the second sector between the direction change giving means (P). Examples of the transmission device using the former means include a CVT device, a blower device, and a driving device. Examples of the transmission device using the latter means include printing paper, copy paper, building material, and civil engineering material. -A device for conveying food and other industrial products, and a device for supplying power to a system that transmits power via gears, rollers, transmission belts, etc.

The transmission body (B) of the present invention is in a closed loop shape. In the transmission apparatus of the present invention, the transmission body (B) is bridged between a plurality of direction change applying means (P). A turning path (R1) for turning the means (P) and a direction change providing means path (R2) between the direction change giving means (P).
The transmission body (B) of the present invention is composed of an array body in which a large number of revolving elements (1) are constrained at the restraining portion (S) by the restraining means (2) and arranged in a closed loop. A first sector having the same curvature as the first arc (A1) is formed in the path (R1), and a second sector (A2) having the same curvature as the second arc (A2) is formed in the path (R2) between the direction change imparting means. Two sectors are formed.
The swivel (1) and the restraining means (2) constituting the transmission body (B) will be described in detail later.

[Route form]
-1-
In the transmission device of the present invention,
(X) The turning path (R1) is formed in a first arc (A1) that protrudes from the center of the turning path (R1) to the outer peripheral side of the transmission body (B),
(Y) The direction change imparting means paths (R2) are convex on the outer peripheral side of the transmission body (B) in all the direction change assignment means paths (R2) or all the direction change assignment means paths In (R2), a second arc (A2) is formed that protrudes toward the inner periphery of the transmission body (B).
Thus, the entire path along which the transmission body (B) travels is formed in an arc (see FIGS. 1 and 2).

-2-
As in (X) above, forming the turning path (R1) into an arc that protrudes outward from the outer periphery of the transmission body (B) with the center of each direction change imparting means (P) as the center point is the conventional tension type Similar to a belt (but see later description). However, with respect to the path (R2) between the direction change imparting means, all the direction change imparting means paths (R2) are formed in an arc that protrudes on the outer peripheral side of the transmission body (B), or all the direction change imparting means The fact that the entire path traveled by the transmission body (B) is formed in the arc by forming the arc convex to the inner peripheral side of the transmission body (B) in the intermediate path (R2) This is the unique and greatest feature of the inventive transmission.
Incidentally, the path (R2) between the direction change imparting means in the V belts V1 to V5 (V belt for the belt CVT) described in the description and section of the prior art is at least a straight line on the tension side in principle. Become.

-3-
In the above, as described in (X) above, “the turning path (R1) is formed into an arc that protrudes from the center of each direction change imparting means (P) to the outer peripheral side of the transmission body (B). This is similar to the conventional tension belt. ”However, the winding angle θ of the transmission body (B) in the turning path (R1) is different from that of the conventional tension belt. Has a great influence on the operational effect, and in that sense, the transmission body (B) is also different from the conventional tension belt in terms of the turning path (R1).

[Detailed description of route traveled by transmission body (B)]
As described above, in the present invention, the transmission body (B) travels along the turning path (R1) formed in the first arc and the path (R2) between the direction change imparting means formed in the second arc. However, at this time, in the state where the transmission body (B) is bridged between the direction change imparting means (P)... And is initially set, the first arc (A1) and the second arc (A2) The transition point (tr) between them is set to be located on a straight line passing through both the center point (O1) of the first arc (A1) and the center point (O2) of the second arc (A2) ( (See FIGS. 1 and 2). Even in a state where the transmission is operated, the same relationship is basically maintained.

(Explanation with reference to figures)
FIG. 1 is a schematic explanatory diagram for explaining the shape of the path drawn by the transmission body (B).
According to the present invention, the transmission body (B) travels smoothly even at the transition point (tr) between the first arc (A1) and the second arc (A2) (there are four locations in FIG. 1). Therefore, energy loss during transmission of force and torque is minimized, which is advantageous in terms of the life of the transmission body (B), and is preferable in terms of noise reduction.

Here, the meanings of lines and symbols in FIG. 1 (and FIG. 2 described later) are as follows.
・ Thick broken line: Turning path (R1) (forming the first arc (A1))
-Thick solid line: Path between direction change grant means (R2) (forms second arc (A2))
・ (O ₁₁ ): The center point of the left first arc (A1) (also the center of the direction change imparting means (P))
・ (O ₁₂ ): The center point of the first arc (A1) on the right (also the center of the direction change imparting means (P))
・ (O ₂ ): Center point of the second arc (A2) (there are two places)
・ (Tr): Transition point between the first arc (A1) and second arc (A2) ・ t: Tangent at the transition point (tr)
・ C: Chord connecting transition points (tr) and (tr) in the left and right inscribed circles
・ Γ: Chord c connecting the transition points (tr) and (tr) in the left and right inscribed circles, and the transition point (tr)
Angle formed by tangent t (radian)
・ R ₁₁ : Radius of the first arc (A1) on the left direction change giving means (P) side ・ r ₁₂ : Radius of the first arc (A1) on the right direction change giving means (P) side ・ R: No. Radius of 2 arcs (A2) ・ β: A line connecting the end points of the second arc (A2) and the center point (O2) of the second arc (A2)
Angle (radian)
・ Θ ₁₁ : Wrapping angle (radian) of the transmission body (B) to the left direction changing means (P)
· Theta _12: transmission member for the right direction changing application means (P) winding angle of (B) (radian)
・ D: Distance between the axes of the two direction changing means (P) and (P) (distance between O _{11 and} O ₁₂ )
・ L: Circumference of transmission body (B) (perimeter based on the position of restraint (S))

(Relational expression / basic expression)
First, the circumference L of the transmission body (B) is expressed by the following formula 1. The first term on the right side of Equation 1 is twice the arc length of the second arc (A2), and the second term on the right side is the arc length of the first arc (A1) on the left side of the direction change imparting means (P) in the figure, The third term on the right-hand side is the arc length of the first arc (A1) on the right-hand side direction imparting means (P) side in the figure.
L = 2Rβ + r ₁₁ θ ₁₁ + r ₁₂ θ ₁₂ (Formula 1)
Next, since the sum of the inner angles of the triangle having (O ₁₁ ), (O ₁₂ ), and (O ₂ ) as the three vertices is π (radian), the following expression 2 is established.
_{β + θ 11/2 + θ} 12/2 = π
That is, 2β + θ ₁₁ + θ ₁₂ = 2π (Formula 2)

On the other hand, the inter-axis distance D is expressed by the following expression 3 (note that the length of the base of the triangle having (O ₁₁ ), (O ₁₂ ), and (O ₂ ) as three vertices becomes the inter-axis distance D). do it).
_{D = (R-r 11)} cos (θ 11/2) + (R-r 12) cos (θ 12/2) ( Equation 3)

(When the gear ratio is 1: 1)
Now, when the gear ratio = 1: 1, that is, when r ₁₁ = r ₁₂ = r and θ ₁₁ = θ ₁₂ = θ, the previous equations 1, 2 and 3 are simplified as follows.
L = 2Rβ + 2rθ (Formula 1a)
β + θ = π (Formula 2a)
D = 2 (R−r) cos (θ / 2) (Formula 3a)
Here, the circumferential length L of the transmission body (B), the inter-axis distance D of the direction change imparting means (P), (P), and the radius R of the second arc (A2) are predetermined set values, and are expressed by the formula 1a, Since there are three variables β, θ, and r in the three expressions of Expression 2b and Expression 3a, β, θ, and r are obtained from the three expressions of Expression 1a, Expression 2b, and Expression 3a.

(When the gear ratio is arbitrary)
-1-
The basic formulas 1, 2, 3 described above, ie
L = 2Rβ + r ₁₁ θ ₁₁ + r ₁₂ θ ₁₂ (Formula 1)
2β + θ ₁₁ + θ ₁₂ = 2π (Formula 2)
_{D = (R-r 11)} cos (θ 11/2) + (R-r 12) cos (θ 12/2) ( Equation 3)
If L, D, and R are set, the variables in equations 1, 2, and 3 are as follows.
Formula 1: β, r ₁₁ , r ₁₂ , θ ₁₁ , θ ₁₂
Formula 2: β, θ ₁₁ , θ ₁₂
Formula 3: r ₁₁ , r ₁₂ , θ ₁₁ , θ ₁₂

-2-
In this case, as can be readily understood from FIG. 1, two upper and lower arcs of the radius R (A2), when determining the inscribed circle of the left radius r ₁₁ inscribed in both the (A2), the inscribed circle The center point (O ₁₁ ) and the winding angle θ ₁₁ are determined. Then, the radius r ₁₂ and the winding angle θ _{12 of the} inscribed circle having the center point (O ₁₂ ) where the distance between the center points is away from the left inscribed circle by D are also determined. If θ ₁₁ and θ ₁₂ are determined, β is immediately determined from Equation 2.

That is, when viewed from a figure formed by two upper and lower arcs of radius R, when the transmission ratio changes, the two inscribed circles that are inscribed in both the upper and lower arcs of radius R become the distance D between the center points. It will swing in the left-right direction while maintaining
Actually, the positions (O ₁₁ ) and (O ₁₂ ) of the two inscribed circles in FIG. 1 (that is, the axis positions of the direction change imparting means (P) and (P)) are fixed. The radius r ₁₁ , r ₁₂ and the wrapping angles θ ₁₁ , θ _{12 of the} left and right inscribed circles change, and the arc length of the first arc (A1) in the turning path (R1) and the path between the direction change imparting means ( arc length of the second arc (A2) is changed in R2), so that the position of the center point of the apparent angle β and the second arc of the second arc (A2) (A2) (O ₂₎ is also changed .

-3-
As described above, in FIG. 1, in the state where the transmission body (B) is bridged between the direction change imparting means (P) and (P) and is initialized, the first arc is operated. (A1) and the transition point between the second arc (A2) (tr) is connecting the center point of the first arc (A1) and (O1) the center point of the second arc (A2) and (O ₂₎ It will be located on a straight line. In other words, the tangent line at the end point (or start point) of the first arc (A1) and the tangent line at the start point (or end point) of the second arc (A2) are the same (become a common tangent line).
As a result, in the case of FIG. 1, smooth transmission of the transmission body (B) is ensured even at the transition points (tr) between the first arc (A1) and the second arc (A2) (there are four locations). You can see that

[Arc curvature]
The curvature of the first arc (A1) is determined by the depth of the V-shaped groove when the transmission body (B) is located when viewed from the center of the direction change imparting means (P).
Regarding the curvature of the second arc (A2), in FIG. 1, the center point (O ₂ ) of the second arc (A2) and the transition points (tr), (tr) in the left and right inscribed circles are defined as three vertices. When a fan-shaped figure with a radius R is considered, the angle γ (radian) between the chord c connecting the two transition points (tr) and (tr) and the tangent t at the transition point (tr) is 0 <γ < π / 2
Set to satisfy the relationship. The preferred range is 0 <γ <π / 4
It is. A more preferable range is π / 200 ≦ γ ≦ π / 6.
And a particularly preferred range is π / 100 ≦ γ ≦ π / 9.
It is.
The curvature of the second arc (A2) in the case of FIG. 2 described later is the same as described above. However, the angle is negative, and there is a restriction that interference does not occur between the upper and lower second arcs (A2).

[Other forms of path drawn by transmission body (B)]
-1-
In the case of FIG. 1 described above, when the path (R2) (two places) between the direction change imparting means is formed in the second arc (A2) that becomes a convex arc on the “outer side” of the transmission body (B). However, it is also possible to form the path (R2) between the direction change imparting means (there are two places) in the second arc (A2) that is a convex arc on the “inner circumference side” of the transmission body (B). .
FIG. 2 is a schematic explanatory view showing this case.

-2-
When this mode is adopted, when the transmission body (B) is first transferred to the direction change imparting means (P), (P), or when the transmission apparatus is in a stopped state, the transmission body (B) is ( There is a risk of reversing and loosening (just like a diaphragm valve). An example of the means for preventing the inversion is to bring an appropriate member such as a rotating body or a guide body into contact with, for example, the position of the white arrow in FIG. 2 with an appropriate urging force. When the transmission body (B) is running with a load applied to the shaft of the direction change imparting means (P) on the driven side, such transmission body (B) does not loosen, but at the start of operation or Since the transmission body (B) may be loosened when the operation is stopped, it is desirable to maintain the contact of the rotating body and the guide body from the white arrow at all times in order to maintain reliable functions.

  Further, the inversion preventing means described above can be provided in the vicinity of the transition point (tr) where the transmission body (B) is released from the contact state with the direction change imparting means (P). In this way, when the inversion prevention means is provided near the transition point (tr), it is preferable to provide the inversion prevention means at a position where the transmission body (B) can be pressed against the direction change providing means (P). The inversion prevention means is preferably provided at all locations near the four transition points (tr) where the transmission body (B) is separated from the direction change imparting means (P). Providing the inversion prevention means at such a position can be used as an alternative installation means in the case where the inversion prevention means cannot be provided at the position of the white arrow.

-3-
In the embodiment of FIG. 2, since the wrapping angles θ ₁₁ and θ ₁₂ of the transmission body (B) with respect to the direction change giving means (P) and (P) can be made large, the direction change giving means (R1) in the turning path (R1) P), (P) and the transmission body (B) are more reliably prevented from slipping, which is preferable in terms of torque transmission between the direction change imparting means (P) and the transmission body (B). However, when the curvature of the arc of the traveling body (B) is approaching the turning path (R1) (first arc (A1)), the path between the direction change imparting means (R2) (second arc (A2) )), It changes to minus (that is, the arc curvature changes to plus-minus-plus-minus during one lap), so it can be used for high speed travel on all routes. It is not necessarily suitable. That is, it can be said that the mode of FIG. 2 is suitable for applications in which strength is given priority and speed may be low.

-4-
The direction change imparting means path (R2) is formed in the second arc (A2) that becomes a convex arc on the "inner circumference" of the transmission body (B) (that is, a concave arc on the "outer circumference"). Figure 2 type transmission body (B)
And the direction change imparting means path (R2) combined with the transmission body (B) of the type shown in FIG. 1 formed in the second arc (A2) which is a convex arc on the "outer peripheral side" of the transmission body (B). These concave arcs and convex arcs can also be used so as to be in contact with each other or close to each other (see (i) and (ii) of FIG. 48).

[Specific structure of transmission body (B)]
-1-
The transmission body (B) is typically composed of an array body in which a large number of revolving elements (1) are constrained at a restraining portion (S) by restraining means (2) and arranged in a closed loop.
More specifically, the individual swirlers (1) restrained in the restraining portion (S) are
(M) It is configured to be swingable around the restraining portion (S), and
(N) Swivel (1) ... a pressure-welded assembly that forms a convex arc on the outer peripheral side or inner peripheral side of the belt when the dorsal abdomen (1b) and (1b) are pressed against each other ( 1n) the structure has a shape or structure that is autonomously formed,
It is particularly preferred that
The restraining means (2) is usually composed of a member different from the slewing element (1), but a part of the slewing part (1) can be obtained by devising the shape or structure of the slewing element (1). Can also be used as the restraining means (2).

-2-
When the transmission body (B) is configured in this way, the transmission body (B) is bridged between the direction change imparting means (P).
(X) The turning path (R1) is transmitted to the center of the center of the turning path (R1) by the unfolding of the swirler (1). B) is formed on the first arc (A1) that is convex on the outer periphery side,
(Y) The path (R2) between the direction change imparting means is overlapped so that the dorsal abdomen (1b) and (1b) of the swirler (1). Or a convex arc on the outer peripheral side of the transmission body (B) in all the direction change imparting means paths (R2) or in all the direction change assignment means paths (R2) ), The second arc (A2) that spans between adjacent direction-changing means (P), (P) Formed into,
It becomes like this.

-3-
When the transmission comprising the direction change applying means (P) and the transmission body (B) is a continuously variable transmission, and the direction change providing means (P) is a pulley having a V-shaped groove. The transmission body (B) also has a size and shape that fits into the V-shaped groove of the pulley.
In the following, unless otherwise specified, the direction change imparting means (P)... Is a pulley having a V-shaped groove, and the transmission body (B) has a size and shape that fits into the V-shaped groove of the pulley. The swirler (1) assembled to the transmission body (B) will also be described in detail by taking as an example the case where the swivel (1) has a size and shape that fits into the V-shaped groove.

[Size and shape to fit into V-shaped groove]
-1-
Here, regarding the transmission body (B) having a size and a shape that fits into the V-shaped groove of the direction change providing means (P), which part of the transmission body (B) is the V shape of the direction change assignment means (P). Describe which part of the groove contacts. In this case, the mode of contact must naturally be able to achieve a smooth shift.

-2-
One of them is that when the direction change imparting means (P) is a pulley, both sides (1a), (1a) of the swivel (1) have an angle corresponding to the sheave angle α (see FIG. 3) of the pulley. It is to form on an inclined surface. Here, “an angle commensurate with the sheave angle α” means an angle that is substantially the same as the sheave angle α. The rotator (1) has one-point contact with the inclined surface of the V-shaped groove of the direction change imparting means (P) in at least one place or one region of the inclined surfaces of both side portions (1a) and (1a). The contact is made in the state of multi-point contact, line contact or surface contact.

It should be noted that, in the description of the direction change imparting means (P) already described, in order to smooth the movement of the swivel (1) at the time of shifting, the sheave surface of the direction change imparting means (P) (fixed sheave ( (Pfs) and the movable sheave (Pms) face each other) can be formed on a slightly convex cone surface, but the following can also be devised.
(I) The sheave surface of the direction changing and imparting means (P) is a cone surface, and the inclined surfaces of both side portions (1a) and (1a) of the swirler (1) are curved slightly convex outward.
(Ii) The sheave surface of the direction change imparting means (P) is formed into a slightly convex cone surface, and the inclined surfaces of the side portions (1a), (1a) of the swirler (1) are slightly convex outward. The curved surface.

-3-
The other is that the individual swirler (1) is restrained by the restraining means (2) at the restraining portion (S), but one or more specific parts of the swirler (1) and the restraining means ( 2) Contact one or more of the specific parts with the V-shaped groove of the direction change imparting means (P).

  Here, regarding the transmission body (B) having a size and a shape that fits into the V-shaped groove of the direction change providing means (P), which part of the transmission body (B) is the V shape of the direction change assignment means (P). Describe which part of the groove contacts. In this case, the mode of contact must naturally be able to achieve a smooth shift.

[Positional relationship between contact part (C) and restraint part (S)]
Next, in the swirler (1) assembled to the transmission body (B), the direction change imparting means (P) in both side portions (1a) and (1a) of the swirler (1) The positional relationship between the contact portion (C) and the restraining portion (S) that restrains the swirler (1) will be described.
With respect to this positional relationship, as shown in the schematic diagram of FIG. 7, the contact portion (C) is positioned on the “peripheral side” of the transmission body (B), and the restraining portion (S) is the transmission body (B It is particularly preferable that the lens is designed to be located on the “inner circumferential side”.
This is because the contact part (C) is located on the inner circumference side of the transmission body (B) and the restraint part (S) is located on the outer circumference side of the transmission body (B), or the same position of the transmission body (B). If the contact part (C) and the restraint part (S) are positioned on the surface, the formation of the second arc (A2) in the path (R2) between the direction change imparting means may become unstable.

[Relationship between the position of the contact part (C) and the contact position of the dorsal abdomen (1b), (1b)]
The virtual plane conceived on the outer peripheral surface side, inner peripheral surface side or cross section of the swirler (1) is the contact position between the dorsal abdomen (1b), (1b) and the position of at least a part of the contact part (C). It is preferable that a plane including
The fact that the position of the contact between the dorsal abdomen (1b), (1b) and the position of at least a part of the contact (C) on such an imaginary plane means that moment force is generated on the swirler (1). The energy loss generated inside the transmission body (B) due to the deviation of the attitude of the swivel (1) can be minimized.
When such a virtual plane is approaching the upper surface of the swivel (1), the influence of the force accompanying the transmission to the second sector can be reduced.
When the above-described virtual plane approaches the restraint means (2) side, when the force accompanying conduction increases, for example, the second sector of the transmission body (B) appears to be the path between the direction change imparting means ( There may be a situation in which the phenomenon of swelling to the outer periphery side and the phenomenon of wilt are alternately and slowly repeated on the outward path and the return path of R2). These phenomena are that the curvature of the second sector becomes large on the return path when the second sector is on the outward path, and the curvature of the second sector increases on the return path when the curvature of the second sector becomes small on the return path. Thus, the change in the curvature of the second sector is caused by a change in the gap of the swivel (1) near the plane of the transmission body (B) and / or a change in the distance between the restraining means (2). It seems to be the cause.
To be sure, the change in the curvature of the second sector is considered to correspond to the curvature of the second arc (A2) because the curvature at the center of the amplitude is considered to be the amplitude phenomenon of the travel path. However, this does not depart from the present invention.

[Relationship between the movement of the swivel (1) and the movement of the restraining means (2)]
-1-
The restraining means (2) is a means for arranging a large number of swirlers (1)... In the restraining portion (S) in a closed loop shape. Therefore, as long as the swirler (1) can be arranged in a closed loop, the movement of the restraining means (2) may be different from the movement of the swirler (1) in principle. However, in this case, every time the transmission body (B) goes around the direction change imparting means (P), etc. (especially in the turning path (R1)), the gap between the swivel (1) and the restraining means (2) Since slipping or slipping may occur, a corresponding energy loss will occur.

  By the way, in the "V3 multilayer hoop-element combination type V belt" described in the section of "Prior art" and "Problems of the prior art", although the elements are restrained by the multilayer hoop, Since the movement of the element and the movement of the multi-layer hoop (and the movement of the hoops of each layer in the multi-layer hoop) are essentially separate, there is always a deviation as the belt goes around the pulley. It collapses into a forward tilt or backward tilt posture, and friction based on slip occurs between the element and the multilayer hoop and between the hoops constituting the multilayer hoop, resulting in energy loss that cannot be ignored.

-2-
Therefore, in the present invention, it is only necessary to design the contact portion (C) to be positioned on the outer peripheral side of the transmission body (B) and the restraint portion (S) to be positioned on the inner peripheral side of the belt as described above. In particular, it is particularly preferable to make a contrivance so that the movement of the swivel (1) and the movement of the restraining portion (S) are not separated.

-3-
In other words, if the swivel (1) is made swingable around the restraining portion (S), the transmission body (B) is bridged between the direction change imparting means (P).
In the turning path (R1), the first arc (which is also the center of each direction change imparting means (P) is obtained by unfolding the swirler (1) which is restrained in the restraining portion (S). Traveling while maintaining a radial positive position as seen from the center point (O1) of A1), and
-In the direction change giving means path (R2), the swirlers (1), which are restrained in the restraining part (S), overlap each other so that the dorsal abdominal parts (1b), (1b) contact each other ( fold) and keep running in a radial position as seen from the center point (O2) of the second arc (A2),
As a result, the movement of the swivel (1) and the movement of the restraint (S) are always "synchronized", eliminating unnecessary movement and unnecessary friction and minimizing energy loss. It becomes.

[Arrangement in which the swirler (1) is arranged in a closed loop]
The transmission body (B) is composed of an array body in which a large number of swirlers (1) are constrained at the restraining portion (S) by the restraining means (2) and arranged in a closed loop. When the restraining means (2) is a separate member from the swivel (1), the side of the swivel (1) is also formed in a shape or structure that can be restrained by the restraining means (2).

[Swivel (1)]
(Both sides (1a), (1a) of the swivel (1))
As already described, both side portions (1a) and (1a) of the swirler (1) are inclined surfaces of the direction change imparting means (P) when the direction change imparting means (P) has a V-shaped groove shape. It becomes a contact part (C).
Both side parts (1a) and (1a) of the slewing element (1) can be made to have a surface with less frictional resistance or the other side to adjust the friction coefficient with the inclined surface of the V-shaped groove of the direction change imparting means (P). In addition, the surface may have a high frictional resistance, or the surface may have a different friction coefficient depending on the direction. For example, it can be a mirror-finished surface; a rough surface; a non-planar processed surface such as irregularities, embossing, grooves, and bulges; Examples of non-planar processed surfaces are # -shaped, wavy, dotted, oblique, T-shaped, cross-shaped, straight in the base end-free end direction, and straight in the thickness direction (back-belly direction). Or curved.
Such a contact part (C) can also be made into one place or multiple places according to the surface state.

(Dorsal abdomen (1b), (1b) of swirler (1))
The dorsal abdomen (1b), (1b) of the swirler (1) can be a flat surface, a curved surface, a step surface or the like.
The surface of the dorsal abdomen (1b), (1b) of the swirler (1) is a mirror-finished surface; rough surface as described in the description of the both side portions (1a) of the swirler (1). Non-planar processed surfaces such as irregularities, embosses, grooves, and bulges can also be used.

(Other ideas)
The rotator (1) can be provided with a through hole, a window, a depression, etc. for various considerations (for example, consideration for stress and weight reduction).

(Shape of swirler (1))
The shape of the swirler (1) in a side view (when viewed from the side portion (1a)) can be a wedge shape, a square shape, a concave lens shape, a convex lens shape, an inverted trapezoidal shape, or the like.
The shape of the swivel (1) when viewed from the front (when viewed from the dorsal abdomen (1b)) is an inverted triangle, an inverted trapezoid, a fan, a baseball, or the like. Since both side portions (1a) and (1a) are surfaces that come into contact with the V-shaped grooves of the direction change imparting means (P), the shape is narrowed toward the inner peripheral side of the belt in a front view.

(Material of the swivel (1))
The material of the swivel (1) can be any material as long as it has the required strength and wear resistance (and oil resistance when used under oil). Examples of materials include metals, plastics, ceramics, carbon materials, natural products (stones, wood materials, bamboo materials, shells, shells, fangs, etc.).

  In the case of plastics, fiber reinforced plastics (FRP) and fiber reinforced thermoplastics (FRTP) are combined with long fibers and short fibers, or a mixture of whiskers, fillers, etc. in the resin is used as the molding material. There are many things. In the case of a carbon material (charcoal, bamboo charcoal, etc.), it can be reinforced by impregnating and curing the resin component. In the case of metals, fibers and carbon can be added to increase strength and other properties. In the case of a wooden material or bamboo, reinforced wood or reinforced bamboo can be used.

The rotator (1) is not only composed of one material, but can also be a composite structure by combining two or more materials. For example, a multilayer structure such as inner-outer, outer layer-inner layer-outer layer. Moreover, even if it is one material, it can also be set as the multilayered structure from which specific gravity differs by the inner side and the surface side as needed. Various coating treatments and plating processes can be applied to the surface of the rotator (1).
When the swivel (1) is a metal, it is often subjected to processing or treatment such as heat treatment, work hardening treatment, and surface treatment.

  The swivel (1) can be composed not only of one piece (one piece) but also of a plurality of pieces. For example, a plurality of pieces sliced in the width direction (side part (1a) -side part (1a) direction) can be prepared, and these pieces can be stacked to form the swirler (1). Also, a plurality of pieces sliced in the thickness direction (dorsal abdominal portion (1b) -dorsal abdominal portion (1b) direction) are prepared, and these pieces can be stacked to form a swirler (1). Each piece in these cases may be made of the same material or different materials.

(Manufacturing method of swirler (1))
There is no limitation on the method of manufacturing the slewing element (1). When the material is a metal, any method including punching, casting, cutting, polishing, bending, folding, and metal injection molding (MIM) can be employed. A method of crushing and deforming the pipe is also possible, and at that time, the core material can be inserted into the pipe and then deformed. It is also possible to employ a method in which a part divided into parts is prepared and then assembled by bonding, fitting, welding or the like.

When the material is plastic, any method including a processing method such as cutting and punching; a molding method such as injection molding, extrusion molding, and compression molding; and an optical shaping method can be employed.
In the case of other materials, a production method or a molding method corresponding to each material is adopted.

[Restraining means (2)]
-1-
The restraining means (2) is a means for restraining the swirler (1) to form a closed loop.
In this case, it is particularly preferable that the swivel (1) swings around the restraining portion (S) with the restraining means (2). When the restraining means (2) is flexible, it can be swung by bending starting from the restraining portion (S).
When the restraining means (2) is a separate member from the swivel (1), the restraining means (2) includes a means using a hinge mechanism, a means using a chain mechanism, a hoop ( That is, a means using a closed loop belt) can be used.

-2-
When the restraining means (2) is a means utilizing a hinge mechanism, the restraining means (2) is often sufficient only with a pin or a combination of a pin and a cylindrical bearing. A bearing hole that is a portion that receives the pin or the cylindrical bearing may be used on the side of the slewing element (1). For the bearing hole, for example, any means such as a method of providing a through hole in a part of the swivel (1), a method of using a pipe, and a method of providing a “6” -shaped portion by bending can be adopted.

  The above pins include rods or pipes whose cross-sectional shapes are circles, ellipses, semicircles, crescents, polygons (triangles, squares, hexagons, octagons, etc.), crosses, stars, etc. Used. Two semi-circular or crescent-shaped rods having a cross-sectional shape may be used in combination. Both ends or one end of the pin may be straight, tapered, straight, or headed. In order to make the pin have a retaining structure, the both ends of the pin may eventually be bulged, fixed with a split pin, clip, screw, or the like, or caulked.

Further, for example, on one side surface around the bearing hole of the slewing element (1), a retaining tab is provided at a position where the detaching prevention function is released when the neighboring slewing elements (1) are tilted by about 50 °. The pin can be prevented from falling off by providing a retaining claw on the other side surface at a position where it can always be prevented regardless of the inclination of the adjacent swivel (1).
At this time, a wall that partially or entirely closes the bearing hole may be provided in place of the retaining tab on the side that always has the function of preventing it from coming off.
The advantage of this method is that the swivel (1) allows the insertion of the pin with one of the bearing holes, but after assembling as the transmission body (B), the pin on both sides of the bearing hole is due to the presence of the claws. In the manufacturing process of the transmission body (B) such as damage to the swivel (1) and the pin due to the insertion of the pin.

-3-
When the restraining means (2) is means utilizing a chain mechanism, parts such as an outer plate, an inner plate, a pin, a bush, and a cylindrical bearing are used in combination.
As a modification when the restraining means (2) is a means using a chain mechanism, the swivel (1) can be communicated with the restraining means (2) via the restraint assisting part (2 ′) ( See FIG.

-4-
As the hoop when the restraining means (2) is a means using a hoop (closed loop belt), a hoop having necessary strength, flexibility, and shape maintenance in the width direction is used.
An example of such a hoop is
-A closed-loop belt made of woven fabric, in which the material corresponding to the yarn in the width direction is a rod-like object or pipe-like object that acts as a pin;
A closed loop belt that is provided with a means for winding a yarn made of high-strength fibers and preventing spreading in the width direction, and has means for connecting or restraining the proximal end side of the swivel (1) thing;
-Hoops such as woven fabric belts made of high-strength fibers, metal hoops, rubber belts with core wires, etc., provided with means for connecting or restraining the proximal end side of the swivel (1);
· Similar to a wristwatch belt and provided with means to connect or restrain the proximal end of the swivel (1);
-A hoop made of a three-dimensional woven fabric, in which a rod-like object or a pipe-like object acting as a pin can be inserted and installed in the gap of the weave of the woven cloth;
Etc. These hoops may be a laminate of two or more layers or a multilayer hoop, but a single layer hoop satisfying flexibility and strength is preferable.

[Specific examples of swirler (1) and restraining means (2)]
Some of the slewing element (1) and the restraining means (2) will be exemplified with reference to the drawings in the following embodiments.

[Assembly of transmission body (B)]
When assembling the transmission body (B) by arranging a large number of swirlers (1), etc. in a closed loop, the swirler (1) is often arranged with a swirler (1) of the same shape ( For example, AAAAA ...) is often preferable in terms of manufacturing cost and quality control of the swivel (1).
However, two or more types of shapes are combined in a certain rule (for example, ABABAB ..., ABCABC ..., AABABAB ...) or in random order, and then the transmission body (B) is often assembled.

  Note that the restraint means (2) restrains the swirler (1) not only in the form of connecting adjacent swirlers (1), (1), but also in a certain swivel, such as skipping one or two. It is also possible to connect one or several forward (or rear) swirlers (1) as viewed from the child (1).

[Device for shifting]
When the transmission device of the present invention is a continuously variable transmission, the direction change imparting means (P) is provided with a V-shaped groove, and the transmission body (B) is provided with V of the direction change imparting means (P). It is usual to use one having a size and shape that fits into the groove.

  In order to change the speed, control is performed to obtain a necessary pressing force (clamping force) so that the transmission body (B) does not slip as much as possible with respect to the direction change imparting means (P). Control refers to control of the gap of the V-shaped groove of the direction change providing means (P). This control is normally performed by hydraulic pressure, and a pressing force by a spring is used in combination as necessary. It is also possible to perform electric control using a motor instead of or together with hydraulic control, and it is also possible to use a spring and a ball (centrifugal weight) that adjusts the V-shaped groove using centrifugal force It is. In addition, instead of or in addition to the control of the gap of the V-shaped groove of the direction change giving means (P), the inter-axis distance of the direction change giving means (P), (P) may be controlled.

In the current belt system CVT, the hydraulic supply system to the movable sheave of the primary pulley and the secondary pulley is
・ One-side pressure method: A method that supplies line pressure to the secondary pulley and shift pressure for shifting to the primary pulley.
・ Both pressure regulation system: Line pressure is supplied to the secondary pulley on the low gear ratio side, gear pressure for shifting is supplied to the primary pulley, and line pressure is supplied to the primary pulley on the high gear ratio side. (Refer to the description on pages 128 to 130 of Non-Patent Document 2 ("Introduction to CVT")). Also in the step transmission, any hydraulic control method including such an existing hydraulic control method can be adopted.

  In the transmission device (continuously variable transmission) of the present invention, as will be described later, the tensile force applied to the transmission body (B) is much smaller than that of the conventional belt (tensile belt). It is possible to reduce the size of the device, reduce the hydraulic force, reduce the hydraulic chamber, and simplify the electronic control program for hydraulic control. Further, a speed change mechanism using an actuator other than the hydraulic pressure can be used. These advantages are that the vehicle weight is reduced and fuel consumption is reduced.

  For example, when applied to CVTs for motorcycles and snowmobiles, the centrifugal force acting on the centrifugal weight (the weight roller that uses centrifugal force) is used to make the gap in the V-shaped groove (P) of the direction change imparting means (P) ( It is also possible to adopt a method of shifting by controlling the fixed sheave (Pfs) and the movable sheave (Pms).

  For example, when applied to a bicycle CVT, the gap of the V-shaped groove of the direction change imparting means (P) is changed manually by a steering wheel operation or a throttle operation or automatically using a sensor to perform a shift. You can also.

  The direction changing means (P)... Mounted on a transmission represented by a continuously variable transmission can be arranged in any manner including horizontal, vertical and diagonal directions.

<Application>
-1-
The transmission device and transmission body of the present invention can be suitably used for applications as exemplified below.
In this case, the present invention is not limited to the case where the transmission device is a transmission and the transmission body of the present invention is a transmission body for a transmission. , Various uses where timing belts, chains, etc. are used).

-2-
・ For automobiles driven by internal combustion engines, motors, compressed air, etc., such as large automobiles, ordinary passenger cars, small passenger cars, mini cars, buses and trucks.
・ For rail cars and endless cars.
・ For motorcycles.
・ Bicycles; Tricycles; Bicycles with electric assist function; For motorbikes.
・ For electric or manual wheelchairs.
・ Agricultural machinery and equipment (cultivators, harvesters (reapers, threshers), etc.), fishery machinery and equipment.
・ Industrial machines such as chemical machinery, textile machinery, metal processing machinery, mining machinery, civil engineering machinery, cargo handling machinery, food processing machinery, lumber / woodwork machinery, papermaking machinery, printing machinery, etc. For instruments.
・ For office and consumer machinery.
・ Elevators; Escalators; Moving walkways; Building lifts, mine lifts; Cranes; Conveyors; Hoisting machines (winches, etc.); Cableways; Lifting devices;
-Ship-related devices, outboard propulsion devices (screw drive devices), aircraft-related devices, power generation systems (including wind and hydraulic power generators), construction or civil engineering-related devices.
・ Power transmission devices not belonging to these

<V belt of V1 to V5 as the prior art>
In the section <Conventional technology> in the background art section, it has been described that among the continuously variable transmissions (CVT), the following V belts of V1 to V5 exist as conventional technologies belonging to the belt system CVT.
V1: Rubber V Belt V2: Multilayer Hoop V Belt V3: Multilayer Hoop-Element Combination V Belt V4: Chain V Belt V5: Composite V Belt

And in the section <Problem of the prior art> in the background art section, these five types of belts V1 to V5 have a common problem due to the fact that all of them are tensile belts. Said that.
Of the five types of belts, the V3 type belt is different from the other four types of belts in that it is a “tensile belt that complementarily uses the compressive force between the elements generated in the slack side path”. Are different from each other, but since the basic is the tension type, there is a limit to the tension type. The belts of the three inventions (i), (ii), and (iii) listed as improved inventions of the V3 type have similar limitations.

<Effects of the present invention>
Hereinafter, the operation or effect of the present invention will be described in detail.
In the following description, in order to avoid confusion in the description, the first sector is expressed as the first arc (A1), the second sector is expressed as the second arc (A2), and the sector and the arc are expressed. May be mentioned without distinction.

[First Feature Point (Part 1): Arc (Arc) Structure]
(Second arc (A2) in the route (R2) between direction change grant means)
-1-
The first characteristic point of the transmission device and transmission body of the present invention is that all the direction change imparting means paths (R2) are formed as arcs (arcs) (second arc (A2)). This feature point is decisively different from the prior art in terms of configuration and also in terms of operational effects.

-2-
In the transmission device of the present invention, a representative example of specific means for forming the path (R2) between the direction change imparting means in the second arc (A2) is configured as follows. That is.
1. The transmission body (B) is composed of an array body in which a large number of swirlers (1)... Are constrained at the restraining portion (S) by the restraining means (2) and arranged in a closed loop. (Here, the restraining means (2) may be formed of a member different from the swinger (1), and a part of the swinger (1) may be used as the restraining means (2).)
2. The individual swirlers (1) restrained in the restraining part (S) are
(M) It is configured to be swingable around the restraining portion (S), and
(N) Swivel (1) ... When the pressure contact is made so that their dorsal abdomen (1b) and (1b) face each other, a convex arc is formed on the outer peripheral side or inner peripheral side of the transmission body (B) The pressed assembly (1n) structure has a shape or structure that is autonomously formed.

[Operational effects based on the first feature point (1)]
-1- (Pressing force by the second arc (A2))
-1.1-
In the present invention having the feature that the path (R2) between the direction change imparting means is formed in the arc (second arc (A2)), the swirler (1) restrained in the restraint portion (S) is the direction. In order to autonomously form the arc-shaped pressure contact assembly (1n) structure (rigid structure) in the path between the switching means (R2), the transmission of force in the path between the switching means (R2) is essentially “ This is done by “pushing force”. For example, when the number of pulleys is two and the path (R2) between the direction change imparting means is composed of the forward path and the backward path, the force is transmitted by “pushing force” in both the forward path and the backward path. As will be described below from various points of view, in the present invention, the tensile force is not so much involved in the transmission of force in the path (R2) between the direction change imparting means.
In order to emphasize the difference from the conventional tension type belt, the “pushing force” is spotted here, but please refer to the explanation in [Discussion from another viewpoint] described later.

  That is, in the present invention, one swirler (1) discharged from the V-shaped groove of the upstream direction change imparting means (P) is an arc formed in the path (R2) between the direction change imparting means. The second arc (A2) consisting of the pressure welding assembly (1n) is pushed from the start end side and occupies the seat of the rotator (1) that was originally on the start end side. As a result, the second arc (A2) is rotated about the center point (O2) of the arc by one swirler (1), and the swivel located on the terminal side of the original second arc (A2) The child (1) is pushed out of the original arc and is caught in the V-shaped groove of the downstream direction change imparting means (P) to rotate the downstream direction change imparting means (P). In this way, the rotational force of the upstream direction change imparting means (P) is converted into the force of rotating the downstream direction change imparting means (P) immediately after being converted into the pressing force by the second arc (A2). Therefore, smooth torque transmission is achieved. A simple illustration is as follows.

-1.2-
In addition, in the present invention, the path (R2) between the direction change imparting means is already rigid in the initial setting stage in which the transmission body (B) is bridged between the direction change imparting means (P) and (P). The arm-shaped second arc (A2) structure is completed. In other words, in the initial setting stage for exerting the clamping force, the upstream direction change imparting means (P) is changed from the upstream direction change imparting means (P) through the “pushing force” by the second arc (A2). It is in a system to transmit torque (ie torque transmission) to (in standby state).

-1.3-
On the other hand, in the belt of V3 described in the section of the prior art, since the space between the element and the hoop is not fixed, no compression force is generated between the elements at the initial setting stage. The “compressive force” that the V3 belt is trying to exert together with the “tensile force” is due to the fact that when the belt starts to operate, the subsequent elements catch up with the preceding elements one after another in the slack side path and become congested. Since a phenomenon in which the compression force between the elements is gradually accumulated from zero to a predetermined level is used, the compression force is generated only after the belt is operated.

-1.4-
In a general tension belt, when the belt is operated with a load on the driven pulley, energy E based on the tension difference ΔT between the tension Tx on the tension side and the tension Ty on the loose side in the reciprocating path is loaded. The force is transmitted when R is overcome.

  The greater the load on the driven pulley, the greater the tension difference ΔT required, so Tx must be increased accordingly. However, the belt has strength limitations ( If the load is too large, it cannot be dealt with.

Here, let us consider in relation to the belt of V3 which is a tension type but generates a compressive force between the elements.
Schematically speaking, the expression of the tensile force in the belt of V3 is caused by the fact that there is a tension difference ΔT between the tension Tx on the tension side and the tension Ty on the loose side, as in a general tension belt. (Energy based on this tension difference ΔT is E). However, in the V3 belt, due to the tension difference ΔT, not only a tensile force but also a compressive force between elements is generated (energy based on the compressive force is assumed to be e). Thus, energy e based on the compressive force is expressed due to the same tension difference ΔT, so that the energy based on the tensile force is reduced to (E−e) (this energy (E−e) is Based on the tension difference ΔT ′ between the newly balanced tension Tx ′ on the tension side and the tension Ty ′ on the loose side).

  Eventually, in the belt of V3, the energy of “(E−e) + e = E” operates the belt against the load R, and compared with a general tension belt that does not express a compressive force. There is no gain or loss in energy, but the energy (Ee) based on the tensile force is based on the tension difference ΔT ′ between the newly balanced tension Tx ′ and the loose tension Ty ′. (Because Tx 'can be smaller than Tx), it is advantageous for belt durability. In this case, if the tension force on the tension side is increased to the upper limit of the tensile strength of the belt, it becomes possible to cope with a larger load.

-1.5-
On the other hand, the second arc (A2) formed in the path (R2) between the direction change imparting means in the present invention is a “pushing force” in both the forward path and the return path (the tensile force is not so related). The force generation mechanism is different from that of a general tension belt. (This will be explained later by changing the viewpoint.)

Also, the force generation mechanism is different from the V3 V-belt that utilizes the tension difference as a tensile force and also exhibits a compressive force between the elements in a complementary manner.
Further, in the present invention, there is no upper limit to the “pushing force” based on the second arc (A2) formed in the path (R2) between the direction change imparting means, so that there is sufficient thrust as the direction change imparting means (P). However, if the restraint means (2) that can withstand the clamping force is selected as the transmission body (B), it can cope with extremely large loads that cannot be handled by the tension belt including the V3 V belt. become.

-2- (Transmission and direction of the pressing force exerted by the second arc (A2))
Next, the transmission and direction of the pressing force exerted by the second arc (A2) in the present invention will be examined. Before that, as an analog for easy understanding, the model shown in FIG. I'll think about it.
As shown in FIG. 4 (i), when a number of spheres connected by a thread having the same length R are arranged on one vertical plane from the same center point (O ₂ ), the spheres 1 to 7 are in close contact with each other. It becomes an aggregate and draws an arc. In this state, if a force Q is input by pressing a new sphere 0 from the left side of the figure and each sphere is moved by one pitch, the force Q is applied from the sphere 1 as shown in FIG. It is transmitted to the sphere 2 one after another, such as from the sphere 2 to the sphere 3 (the direction of the vector at that time is along the tangential direction of the arc), and finally the force Q is output from the sphere 7. At this time, the position of each sphere moves to the right by one pitch, and the position where the aggregate of spheres 1 to 7 occupies the initial coordinates is occupied by the aggregate of spheres 0 to 6. From a different point of view, each sphere is in contact with each other to form an arc-like assembly, so the arc consisting of a sphere array is a transducer that transmits force without waste while changing the direction of the force to the arc direction. Playing a role.
In the model of FIG. 4, it is easy to understand that the arc formed by the sphere assembly is stable, the transmission direction of the force Q is the tangential direction of the arc, and the transmission of the force Q is smooth. It will be possible.

-3- (force applied to each swirler (1) that is a member of the second arc (A2))
In the present invention, since the second arc (A2) composed of the arc-shaped pressure contact assembly (1n) is formed in the path (R2) between the direction change imparting means, the second arc (A2) Considering the transmission of force in detail, keeping in mind the state of -2- above.
First, in the initial setting stage in which the transmission body (B) is bridged between the direction change imparting means (P) and (P), the second arc (1n) consisting of the pressure contact assembly (1n) is already in the inter-pulley path (R2). A2) is formed. The second arc (A2) is maintained even when the driving-side direction change imparting means (P) is driven in a state where a load is applied to the driven-side direction change imparting means (P).

In the second arc (A2) composed of the pressure contact assembly (1n) formed in the path (R2) between the direction change imparting means, as shown in the schematic diagram of FIG. The wedges are arranged in an arc shape (the apex angle of the wedge is 2δ). This state is very similar to the model of FIG.
Thus, also in the present invention, the second arc (A2) having a radius R centered at (O ₂ ) is formed by the press contact assembly (1n) of the slewers (1) as shown in FIG. Since the force Q is transmitted in the tangential direction of the arc, the same behavior as the model of FIG. 4 is performed and the force Q is smoothly transmitted.

Then, what happens if a force directed in a direction other than the tangential direction of the arc is applied to the swirler (1) constituting the pressure welding assembly (1n)? What can occur as such a force is a force acting in a direction in which the swivel (1) jumps out of the arc shown in the schematic diagram of FIG.
In FIG. 6, the swirler (1) sandwiched between the swirlers (1) and (1) located on both sides of the swivel (1) and (1) located on both sides is perpendicular to the slope of the wedge. , Q, it is considered that a component force P directed toward the outer periphery of the transmission body (B) works.

Assuming that the apex angle of the swirler (1) (the angle formed by the slope of the dorsoventral portion of the swirler (1)) is 2δ (1/2 of the angle is δ), FIG.
P / 2 = Q sinδ
Because of the relationship
・ When δ is 0.9 ° (0.005 radians), P ≒ Q / 200,
・ When δ is 1.8 ° (0.01 radians), P ≒ Q / 100,
・ When δ is 3.6 ° (0.02 radians), P ≒ Q / 50
It becomes.

  In other words, even if the component force P that tries to eject the swivel (1), which is a constituent member, of the second arc (A2) composed of the pressure contact assembly (1n) to the outer peripheral side of the belt, the force P is Since it is overwhelmingly smaller than the force Q, it is easy to design the restraining means (2) or restraining portion (S) for restraining the swinger (1) so that it can withstand the P. Incidentally, the force withstanding the above-mentioned P is very small as compared with the tensile resistance required for the conventional tensile type V-belt.

-4- (Restrictions on the manufacture of the swivel (1) and restraint means (2))
As described above, in the present invention, the transmission of the force in the path (R2) between the direction change imparting means is essentially a “pushing force”, and the tensile force is hardly involved. As a source of the force P that prevents the swinger (1) from popping out at the restraint (S) by the restraint means (2), a tensile force may be involved, but the force P is a force Q that is directly involved in the pushing force. It is much smaller than In the present invention, the tensile force as in the case of the conventional tension type V-belt hardly occurs in principle.

  And as the force Q transmitted from one end to the other end of the path (R2) between the direction changing means through the second arc (A2) structure increases, the second arc (A2) structure becomes more stable, The stability of the second arc (A2) is not limited to the manufacturing accuracy of the surface of the swirl (1b) and (1b) of the rotator (1) in principle. ) There is no need for surface contact between the dorsal abdomen (1b) and (1b) only, but two-point contact between the dorsal abdomen (1b) and (1b) between the swirlers (1); Any contact mode is possible as long as the arc structure can be maintained, including two-point or three-point contact with the restraining portion (S).

  By the way, in the conventional V3 V-belt, if the manufacturing accuracy of the dorsal abdominal surface of the element is slightly inaccurate, the structure of the compression body may collapse and the element may be ejected from the hoop.

  The three improved inventions (i), (ii), and (iii) related to the V3 V-belt mentioned in the section of the prior art are the structures that keep in mind that the above-mentioned elements are prevented from being ejected. However, it is impossible to overcome the drawback that the durability of the V3 V-belt depends on the durability of the hoop. In other words, these three improved inventions must balance the advantage of having a convex arc on the slack side path with the disadvantage of sacrificing the durability of the hoop (and thus the entire belt). In addition, it is impossible to form a tight path on a convex arc.

  Furthermore, in the second arc (A2) structure formed in the path (R2) between the direction change imparting means in the present invention, the restraint portion (S) does not have a great tensile force. The restraint means (2) and the restraint portion (S) involved in restraint between them are also less restricted in tensile strength in the production than the conventional tension type V belt including the V3 V belt.

-5 (Tensile stress and compressive stress)
As will be described many times, in the present invention, the arc-shaped pressure contact assembly (1n) structure is formed in the path (R2) between the direction change imparting means by the swirler (1) constrained in the restraint portion (S). Is formed autonomously, the transmission of force in the path between direction change imparting means (R2) is essentially a “pushing force”. Accordingly, the greater the load applied to the driven direction change imparting means (P), the greater the compressive force applied to each of the swirlers (1) constituting the press contact assembly (1n).

When comparing “tensile stress” applied to an object with “compressive stress”, it can be generally said that the compressive strength is much higher than the tensile strength.
For example, pages 107-108 and Figure 4.2.5 of "Osaka Science / Technology Series, Story of Metallic Materials Testing, Issued by the Japanese Standards Association, August 5, 2002, First Edition" , “It is thought that a material with microcracks inside, such as gray cast iron, has a low tensile strength when subjected to tensile stress, but once used for compression, it is not comparable to that when tensile. “High strength values can be obtained.” And “in the case of concrete, it is known that the compressive strength is about 6 times higher than the tensile strength, and the deformation due to compression is very small.” a.

  On page 42 of “Skills Book 20, Metal Material Manual, published by Okawa Publishing Co., Ltd., published on May 15, 2005”, regarding the compression test of metal materials, “The compression test is the opposite of the tensile test. I understand that, but in fact, compression rarely breaks, so there is no standard. "

  Accordingly, in the present invention, since a large tensile force does not act on the swivel (1), there is no need to give much consideration to the tensile force, while a large compressive force is applied to the swivel (1), but the compressive force It is easy to design to withstand.

-6 (Contrast with static arch structure)
In addition, in the field of architecture and civil engineering, bricks and stone arch structures (upward convex arch structures) have been known since the ancient times as means for constructing tunnels, bridges, windows and the like. This arch structure maintains the structure in a static state, and the compressive force generated by the weight of bricks and stones (that is, gravity) is skillfully used to stabilize the structure. Even if a further load is applied to the static arch structure from above, it is still very stable.
However, in this static arch structure, an extremely large force is applied to the leg portion of the arch, and the arch will be broken unless the base portion where the leg portion is located is made to withstand it.

  On the other hand, the second arc (A2) autonomously formed in the path (R2) between the direction change imparting means in the present invention is composed of the pressure contact assembly (1n) of the swirler (1). Similar to the arch structure, it has a stable structure. And the transmission body (B) in the transmission device of the present invention, even when traveling as a closed loop, from the direction change imparting means (P) on the drive side to the path (R2) between the direction change imparting means (second arc (A2)) Rotation of the direction change imparting means (P) on the driven side (that is, between the transmission body (B) and the direction change imparting means (P) in the turning path (R1)). Therefore, even if Q is increased, the second arc (A2) is not destroyed. Rather, the greater the Q, the higher the stability of the second arc (A2).

-7- (Contrast with conventional V3 V belt)
As mentioned earlier, the "compressive force" exhibited together with the tensile force in the V3 V-belt described in the section of the prior art is caused by the congestion of the element in the path where the driven pulley is rotated. This is to help the transmission of torque between the direction change imparting means (P) and (P) by utilizing the phenomenon in which the elements catch up one after another and the compressive force between the elements accumulates.

  At this time, the compressed state does not occur in the steady state, but appears only when the load is generated. The behavior of the element during one rotation of the belt is such that the degree of compression gradually increases from a point just before the belt exits the drive pulley, and becomes a substantially constant compression force when exiting the drive pulley. After passing through the path to the driven pulley and the path to rotate the driven pulley, it gradually becomes smaller before leaving the driven pulley, and when leaving the driven pulley, the compression becomes zero, and the state of zero compression Is analyzed until the compression state begins in the path returning to the driving pulley which is the return path and in the driving pulley. (See Non-Patent Document 3)

  What should be forgotten here is the “tensile force” acting on the hoop that swivels while supporting the element. In order to exert a compressive force between the elements in the V3 V-belt, a tensile force acts on the hoop over the entire circumference (not only in the route where the compression between elements is performed but also in the route where the compression between elements is performed). It must be. In other words, there is no portion where the tensile force of the hoop is zero over the entire circumference. At this time, the behavior of the "tensile force" on the entire circumference of the belt is relatively small from when the belt exits the drive pulley to where the driven pulley turns slightly when the belt is operated under load. It is analyzed that it gradually increases as it is rotated, reaches a maximum at the time when the driving pulley is rotated after leaving the driven pulley, and gradually decreases while the driving pulley is rotated.

  In the V3 V-belt, the path between the pulleys is a straight line. However, it is difficult to apply a compressive force in a straight direction due to an error in dimensional accuracy in the straight line. If there is any dimensional accuracy error, the direction of force will be dispersed and the running will be disturbed, resulting in energy loss. The slight error (accuracy of the element's dorsal surface) will push the element off the hoop. May cause a fatal problem. As described above, the conventional V3 belt has the difficulty of maintaining a straight line while exerting a compressive force, and is quite unreasonable due to its structure.

  The compression behavior of the above elements and the tensile behavior of the hoop in the V3 belt are essentially different from the present invention. The present invention differs in principle and mechanism from the V3 belt (and other conventional tension belts).

(Improved invention of V3)
The inventions of (i), (ii), and (iii), which are improved inventions of V3, are considered only when the tension difference of the multi-layer hoop occurs, considering the analysis of the V belt behavior of V3 described above. It can be seen that a convex-concave arc-like structure, or a convex arc-like structure in only one path.
Therefore, the convex arc-like structure which is supposed to appear due to the above three improved inventions is governed by the tension state of the multilayer hoop, and the arc which appears when considering the tension of the initial strained multilayer hoop. There is a limit to the height setting, and it can be easily imagined that the arc height that appears to be almost linear is acceptable only from the viewpoint of durability and structural problems with the multilayer hoop.

  In addition, in these improved inventions, it is considered that the ultimate purpose is to stabilize the pushing force appearing in the slack side path by the element and to prevent the collapse of the element row, and as a result, to achieve that purpose, the slack is loosened. The arc path is only appearing on the side path, and the arc itself is not intended to be the original aim. In fact, in any of the publications, there is a description that the belt can be interpreted as “a straight line or a structure as close to a straight line as possible in the path between pulleys from the viewpoint of maintaining the durability of the hoop”.

[First feature point (2): arc (arc) structure]
(First arc (A1) in the turning path (R1))
-1-
In the transmission device of the present invention, the rotation path (R1) forms an arc (first arc (A1)), which appears to be similar to the case of using the conventional V1 to V5 V belt.
However, in the transmission of the present invention, the first arc (A1) in the turning path (R1) is constrained by the second arc (A2) in the path (R2) between the direction change imparting means, so that the conventional V1 This is qualitatively different from the turning path in the case of using the V belt of ~ V5.
Therefore, the tensile force acting on the first arc (A1) of the turning path (R1) in the present invention will be examined.

-2-
First, in the case of a conventional tension type V-belt, an extremely large tensile force is applied to the belt so as not to cause slippage with the pulley during operation.
From the standpoint of pulleys, since the two pulleys receive a large force from the belt in a direction approaching each other, a very large force is applied to the shaft of each pulley. Each pulley is also subject to an extremely large bending moment that tries to deform (try to distort) the parallel relationship between the fixed sheave and the movable sheave. There is a tendency for the belt to bite more than necessary and to easily shift to the low side.

Even in the V3 V belt among the conventional tension type V belts, the tensile force acting on the multi-layer hoop is large, so that the driving pulley and the driven pulley receive a large force from the belt toward each other. Therefore, especially on the small-diameter pulley side, the belt is easy to bite deeply into the V-shaped groove of the pulley, the parallelism between the fixed sheave and the movable sheave is lost, and if it is left as it is, a force that shifts to the low side without permission works. This phenomenon occurs.
In order to prevent such an unexpected low-side shift, the hydraulic pressure applied to the pulley must be increased more than necessary, but this is disadvantageous in terms of energy. This is because the belt travels smoothly when the hydraulic pressure is small in a range where no slip occurs between the belt and the pulley, and is advantageous in terms of energy.

-3-
In contrast, in the present invention, the swirler (1) constrained in the constraining portion (S) is autonomously formed into an arc-shaped pressure contact assembly (1n) structure in the path (R2) between the direction change imparting means. Has been. As a result, each direction change imparting means (P) is held by an arc-shaped arm by its pressure contact assembly (1n), and the turn path for turning each direction change imparting means (P). Similarly, the first arc (A1) of (R1) is also configured such that both ends thereof are held by arc-shaped arms.

  Such a state can also be understood from FIG. The two inscribed circles are inscribed in the path surrounded by the first arc (A1) and the second arc (A2) regardless of the speed change operation in FIG. An extremely unreasonable force does not act on the applying means (P), and the gap between the individual swirlers (1) in the state of being sandwiched between the V-shaped grooves of the direction changing applying means (P) in the turning path (R1). Unreasonable powers that try to separate them will not work.

-4-
In FIG. 1, even if a strong force is applied to the swirler (1)... Constituting the first arc (A1) of the inner circumferential circle on the left side, for example, to slide radially outward, The gap between the adjacent swirlers (1)... Does not cause a strong tensile force between the adjacent swirlers (1), and the second arc (A2) in the path (R2) between the direction change imparting means does not work. Change in arc length and angle β, change in arc length and θ11 of the first arc (A1) on the left inner circle, number of swirlers (1) in the second arc (A2) and the first arc (A1) Absorbed by the increase / decrease, after all, it is impossible to try to increase the distance between the individual swirlers (1) in the state of being sandwiched between the V-shaped grooves of the direction change imparting means (P) in the turning path (R1) No power is generated.
That is, if a continuously variable transmission, which is an example of a transmission device, is initially set to the state shown in FIG. 1, the relationship shown in FIG. 1 is maintained even after the continuously variable transmission is operated.

[Second characteristic point: transition point from arc to arc]
The second characteristic point of the transmission device according to the present invention is that the first arc (A1) is in a state where the transmission body (B) is bridged between the direction change imparting means (P). The transition point (tr) between the first arc (A2) and the second arc (A2) is on a straight line that passes through both the central point (O1) of the first arc (A1) and the central point (O2) of the second arc (A2). It is set to be located at.
Therefore, the traveling of the transmission body (B) is the smoothest at the transition point (tr) between the first arc (A1) and the second arc (A2), and the first feature point described above is adopted. The benefits of are maximized.

[Third feature point: Device for positional relationship between contact part (C) and restraint part (S)]
The third feature of the present invention is that, in the rotator (1) assembled to the transmission body (B), as shown schematically in FIG. 7, both side portions (1a) of the rotator (1) are shown. , (1a) where the contact portion (C) with the V-shaped groove of the direction change imparting means (P) is located on the outer peripheral side of the transmission body (B), and the restraint portion (S) that restrains the swirler (1) Is located on the inner peripheral side of the belt.
If it does in this way, formation of the 2nd arc (A2) will be made more stably now in the path (R2) between direction change provision means, and the above-mentioned 1st feature point and also the above-mentioned 2nd feature point The benefits of adopting are maximized.

[Fourth feature point: Device for the relationship between the movement of the swivel (1) and the movement of the restraint (S)]
The fourth feature of the present invention is
In the state that the swivel (1) is swingable around the restraint (S) and that the transmission body (B) is bridged between the direction change imparting means (P).
-In both the turning path (R1) and the direction change imparting means path (R2), the swirler (1) restrained by the restraint (S) is the center point (O1) of the first arc (A1), This means that the vehicle travels while maintaining a positive radial posture as viewed from the center point (O2) of the second arc (A2).

  In this way, the movement of the swivel (1) and the movement of the restraining part (S) are always “synchronized”, and wasteful movement and wasteful friction during belt running are significantly reduced. , Energy loss is minimized. Therefore, the advantages of adopting the first feature point, the second feature point, and further the third feature point are maximized.

[Summary]
Therefore, if the transmission body of the present invention is used, it is freed from various restrictions and limitations in various conventional tension belts that utilize tensile force for power transmission. , Reduction of manufacturing accuracy of transmission member components, extension of the life of transmission members, reduction of size of transmission members, reduction of weight of transmission members, and related members or devices (direction changing imparting means, hydraulic pressure) The control mechanism, the electronic control mechanism, etc.) can be simplified and simplified. As a result, the weight of a vehicle or the like equipped with the transmission body and the transmission device of the present invention can be reduced, fuel consumption can be improved, and vibration and noise can be suppressed.

[Consideration from a different perspective]
Now, in the transmission using a transmission body, transmission is performed because a transmission body drive | works.
The present inventor considers the traveling state of the transmission body including the ring from such a viewpoint, and considers the relationship of the force applied to the closed loop transmission body spanned between the two pulleys in the following, The relationship between the force applied to the disk or ring-shaped transmission body rotated by the pulley is also mentioned.

(1) Interpretation of force in tension type belt
It is considered that the tension type belt has a tensile force A for generating a clamping force (not causing slippage) and a tensile force B for transmitting power.
Since the former tensile force A is not directly involved in the transmission of power, the tensile force B acts as a force for running the belt at the time of load (when operating under a load).
However, the tensile force A must be set or adjusted so that a tensile force corresponding to the load can be obtained according to the magnitude of the load.

-2-
For example, at the time of starting, the rotation of the driving pulley supplied from the power source regulates the belt traveling, and the driven pulley is rotated by the belt traveling so that the traveling state of the belt can be understood. It is thought that it is necessary to interpret the drive pulley as the center.
The driving pulley feeds the belt on the one hand (feeds in) while feeding the belt on the one hand (while feeding it). The driven pulley is fed with the belt sent (sent out) by the driving pulley, and is fed with the belt fed (pulled) by the driving pulley.
That is, when viewed from the belt, on the one hand, the force pushed out of the drive pulley (force in the direction opposite to the tensile force B) is supplied, and on the other hand, the force pulled in the drive pulley (force in the same direction as the tensile force B) is supplied. Can be considered.
Conventionally, the force to be pushed out and the force to be drawn in are interpreted with a driven pulley acting as a force that prevents belt travel due to a load, and the above-described tensile force A is referred to as “slack side tension” and “tension side tension”. And the tensile force B is theorized in a form that does not distinguish.
Even in the case of considering the force to be pushed out and the force to be drawn in accordance with the above-mentioned interpretation of the present inventor, the force by which the tensile force A is pushed out in the downstream path as viewed from the driving pulley (minus tensile force B). The "slack side tension (A-B)" is formed under the influence of the tension, and in the upstream path, the "tension side tension (A + B)" is influenced by the force of the pulling force A (positive tension B). The above-mentioned conventional theory is explained.

-3-
According to the interpretation of the force by the present inventor, it can be understood that the belt of V3 has a structure that can use the pushed-out force that could not be used in the tension type belt as the pushing force. However, it is difficult to theoretically explain the source of the compressive force generated in the loose side path in the belt of V3 by the theoretical interpretation explained only from the conventional tension.

(2) Interpretation of force in a high-level concept transmission body including the transmission body and ring body of the present invention-1-
From a broader perspective, the transmission body used as a power transmission medium from one to the other using the above pulleys is a "flexible structure" such as a tension belt and a "rigid structure" such as a ring body. And can be divided into
It seems that the former flexible structure transmits power only by tension, and the latter rigid structure transmits power only by pushing force. If attention is paid to the fact that, in the side pulley, the transmission body is sent out on the one hand and the transmission body is sent in on the other hand, it can be seen that both travel based on the same mechanism and transmit power.
Therefore, if the driving pulley transmits the transmission body as a “slack side tension” and the transmission force as a “tension side tension”, it refers to the transmission of the tension belt. Similarly, if the sending force and the sending force are understood as they are, the transmission of the force of the ring body will be pointed out.
From this point of view, the superordinate transmission body including the transmission body, tension type belt and ring body of the present invention can be explained by one theory.
By the way, the difference between the two is that only the force sent by the flexible structure is used as the tension (tensile force B) to transmit the force, while the rigid structure sends and sends the force. The force to be used (corresponding to the tensile force B in both cases) is used for transmitting force simultaneously. The rigid structure is expected to work more favorably with respect to the life of the transmission body than the flexible structure in that the rigid structure is distributed in two, that is, a force that sends a force corresponding to the tensile force B and a force that sends it. The
In addition, the flexible structure can receive the clamping force (corresponding to the tensile force A) at many places, whereas the rigid structure does not have a structure that can receive the clamping force only at one place. You can also The flexible structure is expected to work more favorably with respect to the life of the transmission body than the rigid structure in that the clamping force can be distributed and received in many places.
However, the transmission body (B) according to the present invention can simultaneously use the sending force and the sending force at the point where the second sector forms a rigid structure, and the first sector forms a flexible structure. The clamping force can be distributed and received at many points.

  In describing the transmission body of the present invention, there are places where the force to be sent is described as pushing force and the force to be sent as tensile force, but this is a force relationship based on the above superordinate concept. This is because there are cases where it is easier to understand if the description is based on the conventional concept of force relation than the concept.

  Hereinafter, the present invention will be further described with reference to examples.

[Figure Description]
FIG. 8 is a side view showing an example of the transmission body (B) of the present invention, in which it is bridged between two pulleys as the direction change providing means (P), (P) so as to generate a clamping force. The adjusted state is shown.
FIG. 9 is an explanatory view showing an example of a swivel (1) which is a constituent member of the transmission body (B) of FIG.
FIG. 10 is an explanatory view showing an example of the restraining means (2) which is a constituent member of the transmission body (B) of FIG.

[Transmission body (B)]
-1- (swivel (1), restraining means (2))
By cutting a plate of aluminum alloy 2017 (duralumin) as an example of the metal, a swirler (1) having the shape shown in FIG. 9 was produced.
In FIG. 9, (1) is a swivel, (1a) is a side part, (1b) is a dorsoventral part, (1c) is for inserting the pin (2c) of the restraining means (2) of FIG. It is a through hole.

  The dorsal abdomen (1b), (1b) of the swirler (1) has a slightly tapered shape. This is for the purpose of forming the second arc (A2) composed of the compressed assembly (1n) of the swirlers (1)... In the path (R2) between the direction change imparting means.

The swivel (1) has a pin removed from a normal hinge (hinge) having a structure in which two pieces in the shape of “b” and “d” face each other like “bd” and the pin is passed through. This is similar to a structure in which the order is changed to make back-to-back like “db” and the back-to-back portions are integrated and then the pins are re-fitted.
As the restraining means (2), a pin (2c) to be inserted into the through hole (1c) of the swivel (1) was prepared (see FIG. 10).

-2- (Assembly of transmission body (B))
By using a large number of the swirler (1) prepared above and inserting and installing the restraining means (2) (pin (2c)) prepared above into the through hole (1c) Part (S)) and connected in a closed loop. Thereby, the transmission body (B) shown in FIG. 8 was produced.

-3- (Preparation of direction change grant means (P), (P))
Pulley as direction change imparting means (P) consisting of a fixed sheave (Pfs) and a movable sheave (Pms) each having a sheave angle α of 11 ° (the angle of the V-shaped groove is 2α that is twice the sheave angle α) 2 sets were prepared, one pulley was mounted on the driving shaft, and the other pulley was mounted on the driven shaft. A brake load can be applied to the driven shaft. The movable sheave (Pms) made of translucent plastics was used so that the state of the transmission body (B) can be seen over.

-4- (Initial setting)
One of the above pulleys (referred to as a primer pulley) was attached to a drive shaft using a motor as a power source. Further, the other of the pulleys (referred to as a secondary pulley) was attached to a driven shaft that can be loaded by a brake.
Subsequently, the transmission body (B) produced above is fitted into the V-shaped groove of each pulley, and first, the gap between the V-shaped grooves of each pulley is adjusted, and then the distance between the pulleys is adjusted. (B) was tightly bridged so that the V-shaped groove of each pulley was at the same position (that is, the gear ratio = 1: 1), and a clamping force was generated.

-5- (Operation experiment 1)
For the transmission body (B) thus adjusted, the load (brake) to the pulley shaft on the driven side is started from 0 (no load) and A, B, C, with the gear ratio kept at 1: 1. An experiment was carried out in which the vehicle was raised step by step. (Due to the equipment, the load was changed manually.)
The contact surface of the transmission body (B) with each pulley was lubricated with appropriate lubricating oil. As a result, the load (brake) on the driven pulley shaft could be stably and smoothly traveled in any state of A, B and C as well as 0. The vertical movement, stagnation and noise of the transmission body (B) were negligible.

The state of the transmission body (B) during driving is as shown in FIG.
In the left and right turning paths (R1), the first arc (A1) is formed with the center of each of the left and right pulleys as the center point,
-In the path (R2) between the upper and lower direction change imparting means, it is formed in the second arc (A2) with the center point (O ₂ ), (O ₂ ) as the center point,
-The tangent line of both paths (R1) and (R2) at the transition point (tr) of both paths (R1) and (R2) is a common tangent line.

-6 (Operation experiment 2)
Next, by changing the position of the transmission body (B) when fitted into the V-shaped grooves of the left and right pulleys, the gear ratio (driven side transmission body (B) radius: driving side transmission body (B) radius) In addition to the above 1: 1, the low gear ratio (approximately 2: 1) and the high gear ratio (approximately 1: 2) are set, and the load on the driven pulley shaft is set to the above A, B, C Change to the level of the transmission body (B)
An experiment was conducted to operate the.

The contact surface of the transmission body (B) with each pulley was lubricated by appropriately spraying lubricating oil.
Evaluation is not performed for the case where the gear ratio is high and the load on the driven shaft is a high load of level C. This is because the combination of “low gear ratio / high load” is the basis for actual driving, and in some cases, the combination of “intermediate gear ratio / high load” is possible. This is because there is no combination of “speed ratio / high load”.
The results are shown in the following Table 2 together with the results of the operation experiment 1. In Table 2, “O” means “smooth running”, and “-” means “not evaluated”.

[Figure Description]
FIG. 11 is a side view showing an example of the transmission body (B) of the present invention, in which it is bridged between two pulleys as the direction change providing means (P), (P) so as to generate a clamping force. The adjusted state is shown.
FIG. 12 is an explanatory view showing an example of a swivel (1) which is a constituent member of the transmission body (B) of FIG.
FIG. 13 is an explanatory view showing an example of the restraining means (2) which is a constituent member of the transmission body (B) of FIG.

[Transmission body (B)]
-1- (Swivel (1))
By cutting a plate of aluminum alloy 2017 (duralumin) as an example of a metal, a swirler (1) having the shape shown in FIG. 12 was produced. The meanings of the symbols in FIG. 12 are the same as those in the first embodiment.

-2- (Restraining means (2))
As the parts for the restraining means (2) shown in FIG. 13, an outer plate (2a), an inner plate (2b), and a pin (2c) were prepared. The outer plate (2a) and the inner plate (2b) are each provided with two through holes. The center-to-center distance between the two through holes in each of the plates (2a) and (2b) is the pitch.

-3- (Assembly of transmission body (B))
The pin (2c) of the restraining means (2) is inserted and installed in the through-hole (1c) of the swivel (1) using the number of the swirler (1) prepared above and the parts for the restraining means (2). (The insertion installation site becomes the restraining portion (S)) and connected in a closed loop. Thereby, the transmission body (B) shown in FIG. 11 was produced.

-4- (Initial setting)
The same direction change imparting means (P) and (P) as in Example 1 are used as two pulleys, and the transmission body (B) produced above is fitted into the V-shaped groove of each pulley as shown in FIG. By adjusting the gap between the V-shaped grooves of each pulley and then adjusting the inter-shaft distance between the pulleys, the transmission body (B) becomes the same position in the V-shaped grooves of each pulley (that is, the gear ratio = It was adjusted so that a clamping force would be generated.

-5- (Operation experiment 1)
In this state, the same operation experiment 1 as in Example 1 was performed. The state of the transmission body (B) during running was as shown in FIG. The transmission body (B) was able to travel stably and smoothly in any state of A, B, C as well as the load (brake) on the driven pulley shaft being zero. The vertical movement, stagnation and noise of the transmission body (B) were negligible.

-6 (Operation experiment 2)
Subsequently, the same operation experiment 2 as in the case of Example 1 was performed, and the same preferable results as in Table 2 of Example 1 were obtained. In comparison between Example 1 and Example 2, a more preferable result was obtained in Example 1 in which the structure of the restraining means (2) was simple.

[Figure Description]
FIG. 14 is a side view showing an example of the transmission body (B) of the present invention, in which it is bridged between two pulleys as the direction change providing means (P), (P) so as to generate a clamping force. The adjusted state is shown.
FIG. 15 is an explanatory view showing an example of a swivel (1) which is a constituent member of the transmission body (B) of FIG.

[Transmission body (B)]
The swirler (1) shown in FIG. 15 was produced according to FIG. However, in this third embodiment, as shown in FIG. 15, two through holes (1d) are provided in the thickness direction of the swivel (1), and the wires (1e) are passed through the through holes (1d) and (1d). By twisting and squeezing, a space is formed between the adjacent swirlers (1) when the swirlers (1) are in a compressed state, and the path (R2) between the direction change providing means is Two arcs (A2) were formed.
The restraint means (2) is the same as that shown in FIG. 13 according to the second embodiment.
The curvature of the second arc (A2) formed in the path (R2) between the direction change imparting means can be easily changed by exchanging the wire (1e) with various thicknesses. Further, by removing the wire (1e), the path (R2) between the direction change imparting means can be made straight.

  A large number of the above-described swirlers (1) were prepared, and a wire (1e) was inserted into the through hole (1d) of every other swirler (1) and squeezed. Next, by inserting and installing the pin (2c) of the restraining means (2) prepared above in the through hole (1d) of the swivel (1) (the insertion installation site becomes the restraining portion (S)), a closed loop Connected together. Thereby, the transmission body (B) shown in FIG. 14 was produced.

(Initial setting)
Using the same two direction change imparting means (P) and (P) as in the case of Examples 1 and 2, the transmission body (B) produced above is formed in the V-shaped groove of each pulley as shown in FIG. Fit, first adjust the gap between the V-shaped grooves of each pulley, and then adjust the inter-shaft distance between the pulleys so that the transmission body (B) is in the same position in the V-shaped grooves of both pulleys (ie The gear ratio was set to 1: 1 so that it was tightly bridged and adjusted to generate a clamping force.

(Operation Experiment 1)
In this state, the same operation experiment 1 as in Examples 1 and 2 was performed. The state of the transmission body (B) during running was as shown in FIG. The belt was able to run stably and smoothly in any state of A, B, and C as well as the load (brake) on the driven pulley shaft being zero. The vertical movement, stagnation and noise of the transmission body (B) were negligible. In the comparison between Example 1 and Example 2, the result that the Example 1 in which the structure of the restraining means (2) is simple was more preferable.

(Comparison)
For comparison, a test was also conducted in the case where the wire (1e) was not inserted into the through hole (1d) of the swirler (1). In this case, the path (R2) between the direction change imparting means is a straight line, and the second arc (A2) is not formed. The transmission device of this comparative example is a tension belt system, and no pressing force or compressive force acts between the adjacent swirlers (1) in any of the upper and lower direction change imparting means paths (R2). The fact that no pressing force or compressive force is applied between the adjacent swirlers (1) can also be confirmed from the fact that the paper sandwiched between the swirlers (1) falls.
The results of Operation Experiment 1 are shown in Table 3 below.

(Explanation of Table 3)
-Gear ratio-
Set to 1: 1.
−Wound angle θ−
The transmission body (B) is bridged between the pulleys so that the gear ratio is 1: 1, and the transmission body (B) is placed on the pulley (the movable sheave (Pms) is made of translucent resin) with initial tension applied. The contacted part was visually observed and measured with a protractor.

-Vertical movement of transmission body (B)-
Observe the behavior of the traveling body (B) while traveling in the path (R2), (R2) between the upper and lower direction change imparting means, and observe the vertical movement that the tensioning position of the transmission body (B) becomes higher or lower. Observed whether to wake up. The cause of the vertical movement is the non-smoothness of the pulley of the transmission body (B) (that is, the transmission body (B) follows the rotation of the pulley while being bitten into the V-shaped groove near the outlet of each pulley. This seems to be due to the fact that it comes off the V-shaped groove.

(Operation experiment 2)
Subsequently, an operation experiment 2 similar to that in Example 1 was conducted for each case where the diameter of the wire was 0.35 mm, 0.45 mm, 0.70 mm, 0.90 mm, and 1.20 mm. Similar favorable results were obtained.

(Notes on Examples 4 to 28)
In Examples 4 to 28 below, the means for forming the second arc (A2) by the press contact assembly (1n) of the swirler (1) may be omitted or described on the corresponding drawings. Actually, when making the swivel (1), the second arc is devised by providing steps or bulges in the dorsal abdomen (1b), (1b) or installing a member corresponding to the spacer. (A2) is formed.

(Example of hinge type / integrated type)
FIG. 16 is an explanatory view showing an example of the swivel (1). If a large number of the swirlers (1) are connected using pins that are an example of the restraining means (2), they can be assembled to the transmission body (B).

(Example of hinge type / integrated type)
FIG. 17 is an explanatory view showing an example of the swivel (1). If a large number of the swirlers (1) are connected using pins that are an example of the restraining means (2), they can be assembled to the transmission body (B).

(Production Example 1)
Using a steel material (SCM415), a metal injection molding method (commonly known as the MIM method) is used to make the entire circumference of the belt approximately 637.5mm. The swivel (1) has a width of approximately 30mm and a height of approximately 12.5mm. A transmission body (B) was produced by connecting 85 pieces of them as a restraining means (2) using a pin (2c) having a diameter of about 3.65 mm. In the present embodiment, the arc (a2) at the time of producing the transmission body (B) is the pin (2c) which is not illustrated with the swirlers (1) on the outer peripheral side and the swirler (1) on the inner peripheral side. The swirler (1) has a wedge-shaped side cross-sectional shape. The design thickness difference between the outer peripheral side contact position and the outer peripheral side contact position in the wedge shape was set to be about 0.35 mm when the transmission body (B) was manufactured. In addition, the inclination angle of the side surface of the swirler (1) that comes into contact with the pulley as the direction change imparting means (P) is such that the position of contact with the pulley is at the dorsal abdomen (1b), (1b) It was set to be slightly larger than 11 ° so as to be on the outermost circumferential side which is substantially the same as the contact position.

(Operational Experiment of Production Example 1)
This transmission body (B) was requested from Doshisha University's Faculty of Engineering, and the maximum transmission torque, inter-shaft force during rotation, slip ratio, and speed change characteristics were confirmed using a motor-driven CVT testing machine owned by the university. The maximum transmission torque and slip ratio are as follows: input torque = 100 rpm, speed ratio = 1.0, driven side thrust = around 5000 N until the total slip occurs between the transmission body (B) and the pulley. The axial force during rotation is as follows: Input speed = 100, 300, 600, 900, 1200, 1500, 1800 rpm, speed ratio = 1.0, driven thrust = around 4900N, load torque = 0Nm The speed change characteristics were performed under the conditions of input rotation speed = 100 rpm, speed ratio = 0.6 to 1.6, driven side thrust = 3000 N, and load torque = 0 Nm. 51 shows the result of the maximum transmission torque, FIG. 52 shows the measurement result of the interaxial force, FIG. 53 shows the measurement result of the slip ratio, and FIG. 54 shows the result of the shift characteristic.
From these test results, it was confirmed that this transmission body (B) can be used satisfactorily as a substitute for the CVT V-belt, with noise comparable to that of the current belt.

  The pressing force ratio between the pulley side and the secondary side of the V3 V-belt at a gear ratio of 1.0 and a load torque ratio of 0.8 is approximately 1.5 to 1.6 (value read from FIG. 5-5 on Non-Patent Document 1, page 127). In contrast, the ratio of the transmission body (B) was about 1.05.

(Production Example 2)
Using a steel material (SCM415), many swirlers (1) with a width of about 22mm and a height of about 8mm are shown in Fig. 17 so that the entire circumference of the belt is about 616mm by the metal injection molding method (common name: MIM method). 140 of them were prepared, and a transmission body (B) was prepared by connecting them using a pin (2c) having a diameter of about 2.31 mm as the restraining means (2). In this embodiment, the arc (a2) at the time of producing the transmission body (B) is contacted between the rotators (1) on the outer peripheral side and the rotator (1) and the pin (2c) on the inner peripheral side. The side cross-sectional shape of the swivel (1) is a wedge shape. The design thickness difference between the outer peripheral side contact position and the outer peripheral side contact position in the wedge shape was set to be about 0.1 mm when the belt was manufactured. In addition, the inclination angle of the side surface of the swirler (1) that comes into contact with the pulley as the direction change imparting means (P) is such that the position of contact with the pulley is at the dorsal abdomen (1b), (1b) It was set to be slightly larger than 11 ° so as to be on the outermost circumferential side which is substantially the same as the contact position.

  At this time, a claw with a length of about 4.4 mm is provided on one side of the swirler (1) so that the pin (2c) will not come out if the tilt is within about 50 ° in the bearing hole of the adjacent swirler (1). A claw having the same size and shape was provided on the other side so that the pin (2c) did not come out regardless of the tilt angle.

(Operation experiment of Production Example 2)
This transmission body (B) was commissioned to Doshisha University's Faculty of Engineering, and the maximum transmission torque, interaxial force during rotation, and slip ratio were confirmed using a motor-driven CVT testing machine owned by the university. The maximum transmission torque and slip ratio are as follows: input torque = 100 rpm, speed ratio = 1.0, driven side thrust = around 5000 N until the total slip occurs between the transmission body (B) and the pulley. The axial force during rotation is measured under the conditions of input speed = 100, 300, 600, 900, 1200, 1400 rpm, speed ratio = 1.0, driven thrust = around 4900N, and load torque = 0Nm. It was. The result of the maximum transmission torque is shown in FIG. 51, the measurement result of the interaxial force at the time of turning is shown in FIG. 52, and the measurement result of the slip ratio is shown in FIG.
From these test results, it was confirmed that this transmission body (B) can be used satisfactorily as a substitute for the CVT V-belt, with noise comparable to that of the current belt.
By the way, using the formula 3-4 on page 49 of Non-Patent Document 2, the calculated transmission torque is 46.86 Nm when the friction coefficient is 0.1 and the pressing force to the pulley (corresponding to the driven thrust) is 5000 N. . In addition, it is said that in the tension type belt including the normal V3 V belt, the interaxial force increases as the rotational speed increases.

(Example of hinge type / merged type)
FIG. 18 is an explanatory view showing an example of the swivel (1).
In the sixth embodiment, a free end side portion of a swirler having a contact portion (1a) with a pulley as a direction change imparting means (P) and a pin (2c) as an example of a restraining means (2) are inserted. The base end side portion of the slewing element to be made is made separately, and the free end side part and the base end side part are fitted and joined to form a single slewing element (1).
The transmission body (B) can be assembled by connecting a large number of the swirlers (1) produced in this way using pins as restraining means (2).

(Example of hinge type / constraint means (2) and integral type)
FIG. 19 is an explanatory view showing an example of the revolving element (1) and the restraining means (2).
In the seventh embodiment, since the restraining means (2) (pin (2c)) is provided integrally with the swivel (1) itself, the transmission body (B) is prepared without preparing the restraining means (2) separately. Can be produced.

(Example of hinge type / cup type)
FIG. 20 is an explanatory view showing an example of the swivel (1).
The transmission body (B) can be manufactured by connecting a large number of the swirlers (1) using pins that are an example of the restraining means (2).

(Example of internal bending with hinge type / bending type)
FIG. 21 is an explanatory view showing an example of the swivel (1).
FIG. 22 is an explanatory view showing an example of a manufacturing process of the swirler (1) of FIG.
In the ninth embodiment, a flat plate (metal plate) is used as a material, and the swirler (1) shown in FIG. 21 is manufactured according to the steps (a), (b), and (c) in FIG.
The transmission body (B) can be manufactured by connecting a large number of the swirlers (1) of FIG. 21 obtained in this way using pins that are an example of the restraining means (2).

FIG. 23 is an explanatory view showing another example of a punched flat plate used in the manufacturing process of the swirler (1).
FIG. 24 is an explanatory view showing still another example of the punched flat plate used in the manufacturing process of the swirler (1) shown in FIG.
A swivel (1) similar to that shown in FIG. 21 can also be produced by bending a punched flat plate having the shape shown in FIG. 23, or by bending a punched flat plate having the shape shown in FIG. Can also be made.

(Example of external bending with hinge type / bending type)
FIG. 25 is an explanatory view showing an example of the swivel (1).
The swivel (1) of the tenth embodiment is manufactured by bending a punched flat plate having the same shape as that of the ninth embodiment as shown in FIG. 22 (a) in the direction opposite to that in FIG. 22 (b). It is.
The transmission body (B) can be produced by connecting a large number of the swirlers (1) of FIG. 25 obtained in this way using pins that are an example of the restraining means (2).

(Example of internal bending with hinge type / bending type)
FIG. 26 is an explanatory view showing an example of the swivel (1).
The swivel (1) of the eleventh embodiment is the same as that of the ninth embodiment except that a punched flat plate having the shape shown in FIG. It is produced by bending it according to the procedure.
The transmission body (B) can be produced by connecting a large number of the swirlers (1) of FIG. 26 obtained in this way using pins that are an example of the restraining means (2).

(Example of hinge type / bending type + auxiliary cap)
FIG. 27 is an explanatory view showing an example of the swivel (1).
The rotator (1) of the twelfth embodiment has a U-shaped cross section obtained by bending a rectangular plate into which a notch is formed as shown in FIG. It is manufactured by covering a mold member (cap).
The transmission body (B) can be produced by connecting a large number of the swirlers (1) of FIG. 27 obtained in this way using pins that are an example of the restraining means (2).

(Example of hinge type / crush box type)
FIG. 28 is an explanatory view showing an example of the swivel (1).
The swivel (1) of the thirteenth embodiment is produced by flatly deforming a cylindrical object with two plates interposed.
The transmission body (B) can be manufactured by connecting a large number of the swirlers (1) of FIG. 28 obtained in this way using pins that are an example of the restraining means (2).

(Example of hinge type / box type)
FIG. 29 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first part and the second part, and a perspective view of the finished product after combining the first part and the second part. The figure is shown.
In the fourteenth embodiment, the first part at the stage where the rectangular plate is cut so as to have the shape of FIG. 29B (the stage where the foot portion is straight) is the second part of FIG. 29C. Insert the part into the part from above, and finally fold it so that the leg part of the first part in FIG. 29 (b) is widened to produce the finished product of the swivel (1) shown in FIG. 29 (a). is there.
The transmission body (B) can be produced by connecting a large number of the rotators (1) of FIG. 29 (a) obtained in this way using pins that are an example of the restraining means (2). it can.

(Example of hinge type / box type)
FIG. 30 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, and the third component, and the combination of the first component, the second component, and the third component. A perspective view of the finished product is shown.
In Example 15, from both sides of the first part at the stage where the rectangular plate is cut so as to have the shape of FIG. 30B (the stage where the leg portion is straight), FIG. Insert the plate-like second part into the third part of FIG. 30 (d) from above, and finally widen the leg part of the first part of FIG. 30 (b). The finished product of the swirler (1) shown in FIG. 30 (a) is produced.
The transmission body (B) can be manufactured by connecting a large number of the slewing elements (1) of FIG. 30 (a) obtained in this way using pins that are examples of the restraining means (2). it can.

(Example of hinge type / box type)
FIG. 31 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown.

In Example 16, two of the first parts in FIG. 31 (c) and one of the second parts in FIG. 31 (d) are alternately arranged to form the third part in FIG. 31 (e). Inserted from the lower side, and finally inserted the fourth part of FIG. 31 (f) from the side to produce the first finished product of FIG. 31 (a).
Similarly, one of the first parts in FIG. 31 (c) and two of the second parts in FIG. 31 (d) are alternately arranged and inserted into the third part in FIG. 31 (e) from the lower side. Finally, the fourth part shown in FIG. 31 (f) was inserted from the side to produce the second finished product shown in FIG. 31 (b).
The transmission body (B) can be manufactured by connecting the first finished product and the second finished product alternately using pins that are an example of the restraining means (2).

(Example of hinge type / box type)
FIG. 32 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown.

In Example 17, two of the first parts in FIG. 32 (c) and one of the second parts in FIG. 32 (d) are alternately arranged to form the third part in FIG. 32 (e). Inserted from below, and finally inserted the fourth part of FIG. 32 (f) from the side to produce the first finished product of FIG. 32 (a).
Similarly, one of the first parts in FIG. 32 (c) and two of the second parts in FIG. 32 (d) are alternately arranged and inserted into the third part in FIG. 32 (e) from below. Finally, the fourth part of FIG. 32 (f) was inserted from the side to produce the second finished product of FIG. 32 (b).
The transmission body (B) can be manufactured by connecting the first finished product and the second finished product alternately using pins that are an example of the restraining means (2).

(Example of hinge type / box type)
FIG. 33 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown.
In Example 18, two first parts in FIG. 33 (c) and one second part in FIG. 33 (d) are alternately arranged to form the third part in FIG. 33 (e). Inserted from below, and finally inserted the fourth part of FIG. 33 (f) from the side to produce the first finished product of FIG. 33 (a).
Similarly, one of the first parts in FIG. 33 (c) and two of the second parts in FIG. 33 (d) are alternately arranged and inserted into the third part in FIG. 33 (e) from below. Finally, the fourth part shown in FIG. 33 (f) was inserted from the side to produce the second completed product shown in FIG. 33 (b).
The transmission body (B) can be manufactured by connecting the first finished product and the second finished product alternately using pins that are an example of the restraining means (2).

(Example of hinge type / box type)
FIG. 34 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown.

In the nineteenth embodiment, two of the first parts in FIG. 34 (c) and one of the second parts in FIG. 34 (d) are alternately arranged to form the third part in FIG. 34 (e). Inserted from the rear side, and finally inserted the fourth part of FIG. 34 (f) from the side to produce the first finished product of FIG. 34 (a).
Similarly, one of the first parts in FIG. 34 (c) and two of the second parts in FIG. 34 (d) are alternately arranged and inserted into the third part in FIG. 34 (e) from the rear side. Finally, the fourth part shown in FIG. 34 (f) was inserted from the side to produce the second completed product shown in FIG. 34 (b).
The transmission body (B) can be manufactured by connecting the first finished product and the second finished product alternately using pins that are an example of the restraining means (2).

(Example of hinge type / bolt type)
FIG. 35 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown.

In Example 20, two of the first parts in FIG. 35 (c) and one of the second parts in FIG. 35 (d) are alternately arranged, and the third part in FIG. 35 (e) is further arranged. Two pieces were arranged on both ends, and finally the fourth part shown in FIG. 35 (f) was inserted from the side and fixed, thereby producing the first finished product shown in FIG. 35 (a).
Similarly, one of the first parts in FIG. 35 (c) and two of the second parts in FIG. 35 (d) are alternately arranged, and two of the third parts in FIG. 35 (e) are arranged at both ends. The second finished product shown in FIG. 35 (b) was manufactured by placing it on the side and finally inserting and fixing the fourth part shown in FIG. 35 (f) from the side.
The transmission body (B) can be manufactured by connecting the first finished product and the second finished product alternately using pins that are an example of the restraining means (2).

(Example of transmission body (B) that does not use pins)
FIG. 36 is an explanatory view showing an example of a transmission body (B) composed of a connecting body of a revolving element (1) also serving as a restraining means (2), and is a perspective view.
FIG. 37 is an explanatory view showing an example of a sheet-like first component used for manufacturing the swivel (1) also serving as the restraining means (2).
FIG. 38 shows an example of a method for producing a swirler (1) as a finished product from the sheet-like first part of FIG. 37 and a second part that plays a role of a core prepared separately. It is explanatory drawing.

  A space is created by bending the long sheet-shaped first part with slits of FIG. 37 (a) one after another along the folding line and transforming it into a three-dimensional shape, and then a core prepared separately in that space. 36. The constraining means shown in FIG. 36 is manufactured by sandwiching the plate-like second part that plays the role of the body as shown in FIG. 38A and finally joining both ends of the concatenated body. (2) A transmission body (B) consisting of a combined slewing element (1) was prepared. In this transmission body (B), no pins are used.

The transmission body (B) that does not use the pin as described above,
Using the sheet-like first part of FIG. 37 (b) and the plate-like second part that plays the role of the core prepared separately, according to the assembly method of FIG. 38 (b), or
Using one set of sheet-like first parts in FIG. 37 (c) and a plate-like second part that plays a role of a core prepared separately, FIG. 38 (c) or FIG. According to the assembly method of d)
It can also be produced. The assembling method of FIG. 38 (d) is arranged using FIG. 37 (c) so that the restraining portions (S) are opposite to those of FIG. 38 (c).

(Example of swirler (1) made of multiple pieces)
FIG. 39 is an explanatory view showing an example of the swirler (1) made of a plurality of pieces.
In the twenty-second embodiment, two types of parts, a first part on both ends and a second part arranged between the first part and the first part on both ends, are prepared for making the swivel (1). Is used.

  The transmission body (B) is manufactured by using the pin (2c) as the restraining means (2). The first parts are located at both ends of the assembled swivel (1) and come into contact with the V-shaped grooves of the direction change imparting means (P). The length in the circumferential direction of the conductor of the first component is ½ of the length in the circumferential direction of the second component. Since the second part is in contact with the front and rear of the parts in the same row in the circumferential direction, the length in the circumferential direction on the outer circumferential side is smaller than that on the inner circumferential side so that an arc is formed by the contact. It is getting longer. In the second part, no contact is made for arc formation.

(Example of single leg type swivel (1))
FIG. 40 is an explanatory view showing an example of a single leg type swivel (1) and is shown in a perspective view.
In Example 23, the transmission member (B) can be produced by using a restraint means (2) utilizing a chain mechanism.
In the second embodiment described above, as shown in FIG. 12, the transmission body (B) is manufactured using the single-leg type swivel (1) shown in FIG.

(Example of a two-leg swivel (1))
FIG. 41 is an explanatory view showing an example of a two-leg type swivel (1), and is shown in a perspective view.
In Example 24, the transmission member (B) can be produced by using a restraining means (2) that utilizes a chain mechanism.

(Example of one-leg swivel (1) + ring-shaped restraining means (2))
FIG. 42 is an explanatory view showing a state in which the transmission body (B) is manufactured using the single leg type swivel (1).
The transmission body (B) shown in FIG. 42 (b) is produced by assembling the rotator (1) shown in FIG. 42 (a) and using the square ring as the restraining means (2). can do.

(Example of two-legged swivel (1) + hoop-like restraining means (2))
FIG. 43 is an explanatory view showing a state in which a transmission body (B) is produced using a two-legged type swivel (1).
A transmission body (B) shown in FIG. 43 (b) is produced by assembling using the multi-layer hoop as the revolving means (1) shown in FIG. 43 (a) and the restraining means (2). be able to.
43 (a) is used as the swivel (1), and the metal band-like hoop of the watch is used as the restraining means (2) to assemble the transmission shown in FIG. 43 (c). The body (B) can be produced.

(Example of hook type)
FIG. 44 is an explanatory view showing an example of the swivel (1), and is shown in a perspective view.
The transmission body (B) can be produced by using the hoop as the restraining means (2) not shown in the figure.

(Example of band type)
FIG. 45 is an explanatory view showing an example of the swivel (1), and is shown in a perspective view.
The transmission body (B) can be produced by using the hoop as the restraining means (2) (not shown) of the swivel (1) shown in FIG.

Reference example 1

FIG. 46 is an explanatory view showing a procedure for producing the hinge-type rotator (1) of the present invention using a commercially available hinge that can be easily obtained, and is shown in a front view and a side view.
In FIG. 46, (i) shows a commercially available hinge (hinge), (ii) shows a state after the head of the pin of the hinge is shaved, and (iii) shows left and right parts with the pin removed. (Iv) shows a state in which the swivel (1) is completed by fixing the back-to-back portions after cutting the side portions and the pin insertion portions.

FIG. 47 is an explanatory view showing an example of the transmission body (B), and shows a state where it is bridged between two pulleys as the direction change providing means (P), (P).
The transmission body (B) in FIG. 47 is manufactured using the swivel (1) in FIG. 21 according to the ninth embodiment and the pin (2c) as an example of the restraining means (2).

  48 shows a path (R2) of the type shown in FIG. 1 in which the path (R2) between the direction change imparting means is formed as a convex arc on the outer peripheral side of the transmission body (B) and / or the path (R2) between the direction change imparting means. 3 is an explanatory diagram showing an example of how to use the transmission body (B) of the type shown in FIG. 2 in which a convex arc is formed on the inner peripheral side of the transmission body (B). However, the direction change providing means (P) is not shown.

48 (i) shows a case where one transmission body (B) of the type shown in FIG. 1 is used in combination with one transmission body (B) of the type shown in FIG. 2, and FIG. 48 (ii) shows that of the type shown in FIG. When two transmission bodies (B) and one transmission body (B) of the type shown in FIG. 2 are used in combination, FIG. 48 (iii) is used by combining two transmission bodies (B) of the type shown in FIG. 48 (iv) shows a case where one transmission body (B) of the type shown in FIG. 2 is used in combination with a roll.
The usage of FIG. 48 can be adopted when an arbitrary processing is performed on an arbitrary sheet material such as paper, woven fabric, plastic sheet, and metal sheet.

(Another example of swirler (1))
FIG. 49 is an explanatory view showing another example of the swivel (1), and is a partial view of a side view. An alternate long and short dash line in the drawing indicates that the lower side is not shown.
49 (a), (b), and (c) show a case where two types of swivels (1) are used alternately. 49 (d) and 49 (e) show the case where the swivel (1) having a bent or curved shape in a side view is used.

(Another example of restraint means (2))
FIG. 50 is an explanatory view showing another example of the restraining means (2).
This restraining means (2) uses a chain mechanism, but is provided with a restraint assisting part (2 ') so that the swivel (1) can be restrained by the restraint assisting part (2'). It is. Since this embodiment can be provided with two swirlers (1) in one unit of the restraining means (2), the swirler (1) can have a thin thickness between the dorsal belly. .

(Operation experiment)
When the transmission body (B) produced in Production Example 2 of Example 5 is laid over a roller with a diameter of about 100 mm as the direction change imparting means (P), and adjusted to generate a clamping force, it is rotated smoothly. Rotated.

(Operation experiment)
A gear (B) having a diameter of about 100 mm as the direction change imparting means (P) using the transmission body (B) produced in Production Example 2 of Example 5 (the tooth shape and the number of teeth are set so as to mesh with the contact portion of the transmission body (B). It turned smoothly when it was spread over and rotated.

FIG. 1 is a schematic explanatory diagram of the shape of the path drawn by the transmission body (B). FIG. 2 is a schematic explanatory diagram of another form of the path drawn by the transmission body (B). FIG. 3 is an explanatory view showing an example of a pulley as the direction change providing means (P) having a V-shaped groove. FIG. 4 is a model for explaining the transmission and direction of the pressing force exerted by the second arc (A2). FIG. 5 is a schematic diagram of the second arc (A2). FIG. 6 is a schematic diagram showing the force acting on the swirler (1) constituting the compression assembly (1n). FIG. 7 is a schematic diagram showing the positional relationship between the contact portion (C) and the restraint portion (S). FIG. 8 is a side view showing an example of the transmission body (B) of the present invention, in which it is bridged between two pulleys as the direction change providing means (P), (P) so as to generate a clamping force. The state is shown. FIG. 9 is an explanatory view showing an example of a swivel (1) which is a constituent member of the transmission body (B) of FIG. FIG. 10 is an explanatory view showing an example of the restraining means (2) which is a constituent member of the transmission body (B) of FIG. FIG. 11 is a side view showing an example of a transmission body (B) according to the present invention, which generates a clamping force by bridging between two pulleys as direction change imparting means (P) and (P). The state of doing so is shown. FIG. 12 is an explanatory view showing an example of a swivel (1) which is a constituent member of the transmission body (B) of FIG. FIG. 13 is an explanatory view showing an example of the restraining means (2) which is a constituent member of the transmission body (B) of FIG. FIG. 14 is a side view showing an example of the transmission body (B) of the present invention, which generates a clamping force by bridging between two pulleys as direction change imparting means (P) and (P). The state of doing so is shown. FIG. 15 is an explanatory view showing an example of a swivel (1) which is a constituent member of the transmission body (B) of FIG. FIG. 16 is an explanatory view showing an example of the swivel (1). FIG. 17 is an explanatory view showing an example of the swivel (1). FIG. 18 is an explanatory view showing an example of the swivel (1). FIG. 19 is an explanatory view showing an example of the revolving element (1) and the restraining means (2). FIG. 20 is an explanatory view showing an example of the swivel (1). FIG. 21 is an explanatory view showing an example of the swivel (1). FIG. 22 is an explanatory view showing an example of a manufacturing process of the swirler (1) of FIG. FIG. 23 is an explanatory view showing another example of a punched flat plate used in the manufacturing process of the swirler (1). FIG. 24 is an explanatory view showing still another example of the punched flat plate used in the manufacturing process of the swirler (1). FIG. 25 is an explanatory view showing an example of the swivel (1). FIG. 26 is an explanatory view showing an example of the swivel (1). FIG. 27 is an explanatory view showing an example of the swivel (1). FIG. 28 is an explanatory view showing an example of the swivel (1). FIG. 29 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first part and the second part, and a perspective view of the finished product after combining the first part and the second part. The figure is shown. FIG. 30 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, and the third component, and the combination of the first component, the second component, and the third component. A perspective view of the finished product is shown. FIG. 31 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown. FIG. 32 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown. FIG. 33 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown. FIG. 34 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown. FIG. 35 is an explanatory view showing an example of the swivel (1), and is a perspective view of each of the first component, the second component, the third component, and the fourth component, and the first component, the second component, and the second component. The perspective view of the 1st and 2nd finished product after combining 3 parts and 4th parts is shown. FIG. 36 is an explanatory view showing an example of a transmission body (B) composed of a connecting body of a revolving element (1) also serving as a restraining means (2), and is a perspective view. FIG. 37 is an explanatory view showing an example of a sheet-like first component used for manufacturing the swivel (1) also serving as the restraining means (2). FIG. 38 shows an example of a method for producing a swirler (1) as a finished product from the sheet-like first part of FIG. 37 and a second part that plays a role of a core prepared separately. It is explanatory drawing. FIG. 39 is an explanatory view showing an example of the swirler (1) made of a plurality of pieces. FIG. 40 is an explanatory view showing an example of a single leg type swivel (1) and is shown in a perspective view. FIG. 41 is an explanatory view showing an example of a two-leg type swivel (1), and is shown in a perspective view. FIG. 42 is an explanatory view showing a state in which the transmission body (B) is manufactured using the single leg type swivel (1). FIG. 43 is an explanatory view showing a state in which a transmission body (B) is produced using a two-legged type swivel (1). FIG. 44 is an explanatory view showing an example of the swivel (1), and is shown in a perspective view. FIG. 45 is an explanatory view showing an example of the swivel (1), and is shown in a perspective view. FIG. 46 is an explanatory view showing a procedure for producing the hinge-type swivel (1) of the present invention using a commercially available hinge, and is shown in a front view and a side view. FIG. 47 is a side view showing an example of the transmission body (B), and shows a state where a clamping force is generated by bridging between two pulleys as the direction change imparting means (P) and (P). It is shown. 48 is an explanatory diagram showing an example of how to use the transmission body (B) of the type shown in FIG. 1 and / or the transmission body (B) of the type shown in FIG. FIG. 49 is an explanatory view showing another example of the swivel (1), and is a partial view of a side view. FIG. 50 is an explanatory view showing another example of the restraining means (2). FIG. 51 is a graph showing the result of the maximum transmission torque, which is an operation test result of the transmission body (B) of Production Examples 1 and 2 in Example 5. The vertical axis represents efficiency, and the horizontal axis represents load torque. FIG. 52 is a graph showing the results of an operation experiment of the transmission body (B) of Production Examples 1 and 2 in Example 5, and showing the measurement result of the interaxial force at the time of turning. The vertical axis represents the interaxial force, and the horizontal axis represents the input rotational speed. FIG. 53 is a graph showing the results of the operation of the transmission body (B) of Production Examples 1 and 2 in Example 5 and the result of the slip ratio. The vertical axis represents the slip ratio, and the horizontal axis represents the load torque. FIG. 54 is a graph showing the results of the transmission characteristics of the transmission body (B) produced from the slewing element (1) having a width of about 30 mm in the fifth embodiment. The vertical axis represents the number of rotations, and the horizontal axis represents the measurement time.

Explanation of symbols

(1)… swivel,
(1a) ... side part, (1b) ... dorsal abdominal part, (1c) ... through hole, (1d) ... through hole, (1e) ... wire,
(2)… restraining means,
(2a) ... outer plate, (2b) ... inner plate, (2c) ... pin,
(2 ')… restraint assisting part,
(P)… Direction change granting means,
(Pfs)… fixed sheave, (Pms)… movable sheave,
(B) ...
(S) ... restraint part,
(C)… contact part,
(R1) ... turn path,
(R2) ... Route between direction change grant means,
(A1) ... First arc,
(A2) ... Second arc,
(O11), (O12) ... The center point of the first arc (A1),
(O2)… The center point of the second arc (A2),
(tr): Transition point between the first arc (A1) and the second arc (A2)

Claims (7)

It consists of a plurality of direction change giving means (P) and a direction change giving means (P).
The transmission body (B) is a closed loop comprising a turning path (R1) for turning each direction change giving means (P), and a direction change giving means (P)... In a transmission that travels on a route,
(X) The turning path (R1) is formed in a first arc (A1) that protrudes from the center of the turning path (R1) to the outer peripheral side of the transmission body (B),
(Y) The direction change imparting means paths (R2) are convex on the outer peripheral side of the transmission body (B) in all the direction change assignment means paths (R2) or all the direction change assignment means paths In (R2), a second arc (A2) is formed that protrudes toward the inner periphery of the transmission body (B).
Therefore, the entire path traveled by the transmission body (B) is formed in an arc,
A transmission device characterized by. In the transmission body (B), a large number of swirlers (1) are restrained by the restraining means (2) at the restraining portion (S), and the swirler (1) and the restraining means (2) are all synchronized. Comprising an array arranged in a closed loop traveling along a route, and
In the state where the transmission body (B) is bridged between the direction change giving means (P).
(X) The turning path (R1) is a transmission body with the center of the turning path (R1) as a center point by the unfolding of the swirler (1). (B) is formed on the first arc (A1) that protrudes to the outer peripheral side,
(Y) The direction change imparting means path (R2) overlaps so that the swirlers (1), which are restrained in the restraining part (S), contact each other between the dorsal abdominal parts (1b), (1b). (Folded), a convex arc is formed on the outer peripheral side of the transmission body (B) in all the paths (R2) between the direction change imparting means, or transmission in all the path (R2) between the direction change imparting means The pressure welding assembly (1n) structure that forms a convex arc on the inner peripheral side of the body (B) is autonomously formed, so that the second changeover means (P), (P) between the adjacent direction change imparting means (P) Formed in the arc (A2),
Therefore, the entire path traveled by the transmission body (B) is formed in an arc,
The transmission device according to claim 1. The direction change imparting means (P) is a pulley having a V-shaped groove,
The transmission body (B) has a size and a shape that fits into a V-shaped groove of the direction change providing means (P), and
The transmission device comprising the direction change providing means (P) and the transmission body (B) is a continuously variable transmission;
The transmission device according to claim 2. A plurality of direction change granting means (P)... A turn path (R1) that turns each direction change grant means (P) by passing between them, and a direction change grant means (P). A closed loop transmission body (B) for traveling along the intermediate path (R2),
In the transmission body (B), a large number of swirlers (1) are restrained by the restraining means (2) at the restraining portion (S), and the swirler (1) and the restraining means (2) are all synchronized. Comprising an array arranged in a closed loop traveling along a route, and
Individual swirlers (1) restrained in the restraint (S)
(M) It is configured to be swingable around the restraining portion (S), and
(N) When the swirler (1) is pressed against each other so that their dorsal abdomen (1b) and (1b) face each other, a convex arc is formed on the outer peripheral side or inner peripheral side of the transmission body (B). The pressure contact assembly (1n) has a shape or structure that is autonomously formed,
In a state where the transmission body (B) is bridged between the direction change grant means (P).
(X) The turning path (R1) is transmitted to the center of the center of the turning path (R1) by the unfolding of the swirler (1). B) is formed on the first arc (A1) that protrudes to the outer peripheral side,
(Y) The direction change imparting means path (R2) is overlapped so that the swirlers (1). (Folded), a convex arc is formed on the outer peripheral side of the transmission body (B) in all of the direction change imparting means paths (R2), or in all the direction change assignment means paths (R2) (B) The second arc that hangs between adjacent direction-changing imparting means (P) and (P) by autonomously forming a pressure welding assembly (1n) structure that becomes a convex arc on the inner circumference side of (B) Formed in (A2),
Therefore, the entire path traveled by the transmission body (B) is formed in an arc,
As a result, the array forms a first sector having the same curvature as the first arc (A1) in the turning path (R1), and in the path (R2) between the direction change imparting means. Forming a second sector having the same curvature as two arcs (A2);
A transmission characterized by   In the swirler (1) assembled to the transmission body (B), the swirler (1) contacts the direction change imparting means (P) at the contact portions (C) of both side portions (1a) and (1a). The contact portion (C) is positioned closer to the outer peripheral side of the transmission body (B) than the restraint portion (S) restraining the swirler (1). Item 4. The transmission body according to Item 4. In a state where the slewing element (1) is made swingable around the restraining part (S), and the transmission body (B) is bridged between the direction change imparting means (P).
In-turn route (R1), by the swirl member being constrained (1) ‥ is deployed (Unfold) in the restrained portion (S), viewed from the center point of the first arc (A1) (O ₁₎ Running while maintaining a radial positive attitude, and
-In the direction change giving means path (R2), the swirlers (1), which are restrained in the restraining part (S), overlap each other so that the dorsal abdominal parts (1b), (1b) contact each other ( (folded) and kept in radial contact as seen from the center point (O ₂ ) of the second arc (A2) in a pressure contact state,
The transmission body according to claim 4. The direction change imparting means (P) is a pulley having a V-shaped groove,
The transmission body (B) has a size and a shape that fits into a V-shaped groove of the direction change providing means (P), and
The transmission body (B) is a transmission body for a continuously variable transmission;
The transmission body according to claim 4.