JP2517123B2 - V belt - Google Patents

Description

The present invention relates to a V-belt applied to continuously variable transmission and the like.

(Prior Art) As a conventional V belt, for example, Japanese Patent Laid-Open No. 61-84436
There is one shown in Japanese Patent Publication.

The V-belt shown therein is composed of an endless chain in which a large number of link plates are sequentially connected by pins and a friction block attached to the chain, and the chain penetrates a window portion provided in the friction block. ing.

(Problems to be solved by the invention) However, in such a conventional V-belt, the dimensional relationship in the width direction between the window portion of the friction block and the link of the chain (the dimensional relationship in the width direction of the V-belt constituent elements). Therefore, if the gap between the two is small, there is a problem that the link plate and the friction block collide with each other and the belt durability deteriorates.
When the belt travels between the pulleys, the friction block moves freely in the width direction to generate noise and wear, and when the belt is wound around the pulleys, collisions occur, which reduces the durability of the pulleys. There was a problem.

Also, in the case of a V-belt in the form of a combination of a friction block having a chain insertion portion in which a portion on the tapered surface side is opened and a chain having a link plate in which a concave portion is formed in the pin axial direction, The dimensional relationship between the width of the concave portion of the link plate and the thickness of the friction block (V
If there is no stipulation (belt running direction dimension relationship of the belt constituent elements), and the difference between the two widths is small, the link plate and the friction block are twisted when meshing with the pulley, and the belt durability is reduced. However, if the difference in width between the two is too large, when the V-belt travels between the two pulleys, the friction block moves in the belt travel direction, which causes noise and wear. There is a problem that the durability of the pulley is deteriorated because a collision occurs when it is wound around the pulley.

The present invention has been made focusing on such a problem,
An object of the present invention is to improve belt durability, prevent noise and wear, and pulley durability in a V-belt by combining a chain with a friction block having an open chain insertion portion.

(Means for Solving the Problems) In order to solve the above problems, the V belt of the present invention is
The dimensional relationship between the width of the concave portion of the link plate and the thickness of the friction block, which is the dimensional relationship of the belt constituent elements in the belt running direction, is defined as the minimum difference within the range where twisting does not occur during meshing of the pulleys.

That is, it is a V-belt, each of which is composed of a fixed cone member and a movable cone member, and is spanned between a drive pulley and a driven pulley in which the axial positional relationships of both cone members are opposite to each other. Two or more rows of chains in which a number of link plates endlessly connected to each other by pins are formed on the edges of the link, and there are taper surfaces on both sides that contact the pulleys, and the link plate has the above-mentioned concave shape. In a V-belt constituted by a combination with a friction block having a chain insertion portion capable of receiving the portion from the tapered surface side, the relationship between the width W ₁ of the concave portion of the link plate and the thickness W ₂ of the friction block the, [delta] _max; V of the drive pulley and the driven pulley occurs between the movable conical member of the drive pulley and the driven pulley is moved from the minimum speed ratio to the maximum speed ratio Maximum misalignment at the center of the groove S; Distance between the center axes of the drive pulley and driven pulley W; Width of the friction block inserted in the concave part of the link plate π-2ψ; When maximum misalignment occurs To the drive pulley of
Belt wrap angle π + 2ψ; V belt wrap angle around driven pulley, It is characterized that it is set to be given in the relationship of.

(Operation) While the drive pulley and the driven pulley shift from the minimum gear ratio to the maximum gear ratio, the center deviation amount of the center position of the V-shaped groove of both pulleys fluctuates, and becomes the maximum amount at a predetermined gear ratio.

At this maximum misalignment amount, the above formula is used to obtain the relationship between the width W ₁ of the concave portion of the link plate and the thickness W ₂ of the friction block in which the link plate meshing with the pulley and the friction block are not twisted. The difference between the two is set by.

Therefore, even if the amount of misalignment of both pulleys reaches the maximum value, the link plate and the friction block are not twisted when meshing with the pulleys, and the belt durability can be improved. Further, when the V-belt travels between both pulleys, the amount of movement of the friction block in the belt traveling direction is restricted to a minimum, so that the difference between the width W ₁ of the concave portion and the thickness W ₂ of the friction block is reduced. The belt noise and the belt wear can be suppressed to be small as compared with the case where the pulley is too large, and further, the deterioration of the pulley durability due to the collision at the time of winding around the pulley can be suppressed.

(Example) Hereinafter, the Example of this invention is described with reference to drawings.

 First, the configuration will be described.

FIG. 1 is a side view of an essential part showing a V-belt of an embodiment, FIG. 2 is a partially cutaway plan view showing a V-belt of an embodiment, FIG. 3 is a sectional view taken along line II of FIG. FIG. 1 is a diagram showing a V-belt type continuously variable transmission to which the V-belt of the embodiment is applied.

In FIG. 4, the drive pulley 1 is composed of a fixed cone member 12 fixed to the drive shaft 11 and a movable cone member 13 provided so as to be movable in the axial direction by hydraulic pressure or the like with respect to the drive shaft 11, and the driven pulley 2 is A fixed cone member 22 fixed to the driven shaft 21 and a movable cone member 23 provided so as to be movable in the axial direction by hydraulic pressure or the like with respect to the driven shaft 21. Then, the conical members 12 and 13 on the driving side and the conical member 2 on the driven side
The axial positional relationships of 2, 23 are opposite to each other, and the conical surfaces 12a, 13a of the driving pulley 1 and the conical surfaces 22a, 2 of the driven pulley 2 are arranged.
The V-belt 3 of the embodiment is stretched over the V-shaped groove formed by 3a.

As shown in FIGS. 1 to 3, the V-belt 3 includes a first chain 31 and a second chain 32, and a large number of friction blocks 33 as constituent elements.

The first chain 31 and the second chain 32 are basically the same, and two rows of outer link plates 301 and 3 are used.
The inner link plates 302 in a row are alternately shifted by 1/2 pitch and are sequentially connected by a joint pin 303 and a rocker pin 304, which form a silent pin, to form an endless shape.

The difference between the outer link plate 301 and the inner link plate 302 is that there is a pin hole that receives only the joint pin 303, or the joint pin 303 and the rocker pin 3
It is only whether there is a pin hole that accepts both 04.

The outer link plate 301, as shown in FIG.
Both ends of the rectangular plate are semi-circular with the center of the pin hole as the center, and both upper edge and lower edge have a rectangular cross section.
305 and 306 are provided respectively. As described above, since the outer link plate 301 and the inner link plate 302 are the same except for the pin holes, the inner link plate 302 is also provided with the concave portions 305 and 306. As shown in FIGS. 2 and 3, the outer link plate 301 and the inner link plate 302 are connected to the joint pin 303 and the rocker pin 304.
After the connection, the joint pins 303 are prevented from coming off by caulking both ends of the joint pins 303.

The friction block 33 is, as shown in FIG.
33a, a pillar portion 33b, and a guide portion 33c. Both sides of the main body portion 33a have tapered surfaces 3 that come into contact with the pulley.
3d and 33e are formed, and the main body portion 33a, the pillar portion 33b, and the guide portion 3 are formed.
Chain insertion part to insert the chain from the outside between 3c
33f and 33g are formed.

Of these, one of the chain insertion parts 33f (or 33g) is
The recesses 305 and 306 are formed to have an insertion width to be inserted and fitted.

Then, as shown in FIG. 1, the link plate 30
The relationship between the width W ₁ of the concave portions 305 and 306 of 1,302 and the thickness W ₂ of the friction block 33 is set as follows.

First, as shown in FIG. 4, V-shaped grooves of the drive pulley 1 and the driven pulley 2 which are generated while the movable conical members 13 and 23 of the drive pulley 1 and the driven pulley 2 move from the minimum gear ratio to the maximum gear ratio. The maximum misalignment amount δ _{max at} the center position of
As shown in FIG. 4 and FIG. 5, the distance S between the central axes of the drive pulley 1 and the driven pulley 2 is set as shown in FIG.
When the wrap angle of the V belt 3 around the drive pulley 1 when the maximum misalignment amount δ _max occurs is π−2ψ and the wrap angle of the V belt 3 around the driven pulley 2 is π + 2ψ, the maximum misalignment is The inclination angle θ of the friction block 33 with respect to the drive pulley shaft at the pulley winding portion is It is represented by.

The width of the friction block 33 inserted into the concave portions 305 and 306 of the link plates 31 and 32 is W (as shown in FIG. 3, the friction block 33 has an upper width W ′ and a lower width W ′). Of the friction block 33. Since W> W ', W is defined as the width of the friction block 33.) As shown in FIG. 6, the inclination angle θ, the friction block width W and the concave shape The relationship between the section width and the block thickness difference W ₁ −W ₂ is It is represented by.

Therefore, according to the above equations (1) and (2), there is a minimum difference that is preferable at the time of running the belt, and the maximum misalignment amount δ.
_When the pulley meshes at the position of the gear ratio where _max occurs, the width W _{1 of} the concave portion that allows the inclination of the friction block 33 to prevent twisting between the chains 31 and 32 and the friction block 33
And the block thickness W ₂ difference W ₁ −W ₂ is Given by the relationship.

 Next, the operation will be described.

(B) At the time of assembling the V-belt The V-belt 3 is assembled as follows. First,
The first chain 31 and the second chain 32 are individually assembled. At this time, the joint pin 303 is prevented from coming off by caulking both ends of the joint pin 303 as described above, and the outer link plate 301 and the inner link plate 3
02 is combined so as not to separate. Next, the first chain 31 and the second chain 32 are respectively inserted from both sides into the chain insertion portions 33f and 33g of the friction block 33 aligned with a predetermined pitch interval. As a result, the first chain 31 and the second chain 32 are assembled to the friction block 33.

That is, the friction block 33 contacts the outer link plate 301 and the inner link plate 302 at the concave portions 305 and 306.

In the assembled state, the first chain 31 and the second chain 32 may come off from the friction block 33. However, if the assembled V belt 3 is wound around the two pulleys 1 and 2, it is wound around. , First chain 31 and second chain 32
Will never fall out.

(B) When using a V-belt While the drive pulley 1 and the driven pulley 2 are shifting from the minimum gear ratio to the maximum gear ratio, the center misalignment amount of the V-shaped grooves of both pulleys 1 and 2 is shown in FIG. Fluctuates as shown, gear ratio
The maximum amount is δ _max at 0.4 and the gear ratio of 2.5.

When this maximum misalignment amount δ _{max is} the minimum difference that is preferable when the belt is running, and the link plates 301 and 302 are concave so that the link plates 301 and 302 meshing with the pulleys 1 and 2 and the friction block 33 are not twisted. The difference between the width W _{1 of the} portions 305 and 306 and the thickness W ₂ of the friction block 33 is set by the above equation (3).

Therefore, even when the amount of misalignment between the pulleys 1 and 2 reaches the maximum value, the link plates 301 and 302 and the friction block 33 do not get twisted when the V belt 3 meshes with the pulleys 1 and 2.

As a result, the forces acting on the V-belt 3 is only the nearly torque accompanied tension and a pulley contact force transmission, for example, W ₁
As in the case where −W ₂ ≈0, the deformation force associated with the twisting is almost eliminated, and the belt durability can be improved.

Further, W ₁ -W ₂ is set to the minimum difference that does not cause twisting, and when the V belt 3 travels between both pulleys 1 and 2,
Since the amount of movement of the friction block 33 in the belt running direction is also restricted to a minimum, belt noise and belt wear can be kept small compared to when the difference between the width W _{1 of the} concave portion and the thickness W ₂ of the friction block is too large. In addition, the deterioration of the pulley durability due to the collision of the V-belt 3 when it is wound around the pulleys 1 and 2 can be suppressed.

The embodiments of the present invention have been described above with reference to the drawings.
The specific configuration is not limited to this embodiment. For example, in the embodiment, the concave portions are provided on both sides of the longitudinal edge portion of the link plate, but the concave portion may be provided only on one edge portion. it can.

(Effects of the Invention) As described above, according to the present invention, in the V-belt formed by the combination of the friction block having the chain insertion portion in the released state and the chain, the dimensional relationship of the V-belt constituent elements in the belt traveling direction is considered. Since the dimensional relationship between the width of the concave part of a certain link plate and the thickness of the friction block is defined as the minimum difference within the range where twisting does not occur when meshing the pulley, the link plate and the friction block will twist when meshing the pulley. The belt durability is improved, and the movement of the friction block when traveling between both pulleys is minimized to prevent noise and wear. The effect of being able to improve the durability of the pulley can be obtained by suppressing the collision to be small.

[Brief description of drawings]

FIG. 1 is a side view of essential parts showing a V-belt of an embodiment, FIG. 2 is a partially cutaway plan view showing a V-belt of an embodiment, and FIG.
FIG. 4 is a cross-sectional view taken along line I-I, FIG. 4 is a diagram showing a V-belt type continuously variable transmission to which the V-belt of the embodiment is applied, and FIG. 5 is a diagram showing dimensional relationships when the misalignment amount is maximum. 6 is a diagram showing the twisted state of the friction block and the chain when the amount of misalignment is maximum, and FIG. 7 is a characteristic diagram of the amount of misalignment with respect to the gear ratio. 1 …… Drive pulley 11 …… Drive shaft 12 …… Fixed cone member 13 …… Movable cone member 2 …… Driven pulley 21 …… Driven shaft 22 …… Fixed cone member 23 …… Movable cone member 3 …… V belt 31 ...... First chain 32 ...... Second chain 301 …… Outer link plate 302 …… Inner link plate 303 …… Joint pin 304 …… Lock pin 305,306 …… Concave part 33 …… Frictional block 33d, 33e …… Tapered surface 33f, 33g …… Chain insertion part

Claims (1)

(57) [Claims] 1. A V-belt, each of which is composed of a fixed cone member and a movable cone member, and is stretched over a drive pulley and a driven pulley in which axial positional relationships of both cone members are opposite to each other. Chains of two or more rows in which a number of link plates in which concave portions in the axial direction of the pin are formed on both or one of the edges are connected endlessly by pins, and taper surfaces contacting the pulley are provided on both sides In the V-belt configured by combining the above concave portion with a friction block having a chain insertion portion that can receive taper from both sides, the width W ₁ of the concave portion of the link plate and the thickness W _{2 of the} friction block relationship, [delta] _max of; occurring between the movable conical member of the drive pulley and the driven pulley is moved from the minimum speed ratio to the maximum speed ratio drive pulley and the driven pulley Of the V-shaped groove at the center position S; the distance between the center axes of the drive pulley and the driven pulley W; the width of the friction block inserted into the concave portion of the link plate π-2ψ; V to the drive pulley when it occurs
Belt wrap angle π + 2ψ; V belt wrap angle around driven pulley, A V-belt characterized by being set so as to be given in the relationship of.