JPH0535225Y2 - - Google Patents

Description

[Detailed explanation of the idea] [Industrial application field]

The present invention relates to a V-type chain belt for power transmission in a belt-type continuously variable transmission that can be used as a transmission for automobiles, etc. More specifically, the present invention relates to a V-type chain belt for power transmission in a belt-type continuously variable transmission that can be used as a transmission for automobiles. This relates to a V-type chain belt for use.

[Conventional technology]

Recently, many belt-type continuously variable transmissions have been proposed as transmissions for automobiles and the like. A belt-type continuously variable transmission is equipped with pulleys having a circumferential groove (V groove) with a V-shaped cross section on one rotating shaft and the other rotating shaft, and a V groove for power transmission between both pulleys.
The belt is tied around. By changing the widths of the V grooves of both pulleys, rotational power is transmitted from one rotating shaft to the other rotating shaft in a stepless manner. Conventionally, as one of the V-type belts used in this type of belt-type continuously variable transmission, a V-type chain belt for power transmission of a type in which a V-type block is attached to a link is known. That is, as shown in FIGS. 38 and 39, a notch (block attachment groove) 07 for attaching a V-shaped block is provided approximately at the center of a link 01 having pin holes 02 at both ends. .
As shown in FIG. 37, the V-shaped block 04 has tapered surfaces 05 on both sides that make frictional contact with the input and output pulleys, and a link hole 06 is formed in the center thereof. Then, as shown in FIGS. 36 and 37, a plurality of links 01 are alternately inserted into the link holes 06 of the V-shaped block and overlapped, and the pins 03 are inserted into the pin holes 02 of each link. A V-type chain belt for power transmission has been proposed in which the belts are connected so as to be articulated and formed into an endless shape, and the notches 07 of the links are engaged with the link holes 06 of the V-shaped block (for example, Jikkosho 39-3919). In addition, a protruding part having a block receiving surface is formed on one edge surrounding the pin hole of the link, and the protruding part is inserted into the link hole of the V-shaped block so that the left and right sides are alternately positioned, and the joint is moved by the pin. A V-type chain belt for power transmission, which can be connected together, has been proposed (for example, Japanese Utility Model Publication No. 13929/1983).

[Problem that the invention attempts to solve]

However, in the V-type chain belt for power transmission configured as described above, stress concentration occurs at the corner 08 of the block mounting groove 07 in the link 01, causing early breakage of the link 01. The reason for this is that, as shown in Fig. 38, (a) the corners 08 of the block mounting grooves 07 have an acute-angled shape, and (b) the chain radial direction in the link body between the block mounting grooves 07 The width dimension is much smaller than the chain radial width dimension W' (diameter of the pin hole edge) at the pin hole edge, and the corner 08 and pin hole 02
This is because the dimension L between them is small. Therefore, there was a problem in that it was difficult to ensure durability due to fatigue failure from the corner 08. Therefore, as one of the above countermeasures, as shown in FIG. A protrusion 011 having a block receiving surface 09 is provided on the inner peripheral side, and the chain radial width dimension W in the link body between the block mounting grooves 07 is set larger than the chain radial width dimension W' at the edge of the pin hole. , corner 08 and pin hole 0
It is conceivable to make the dimension L between the two as large as possible. However, even with the V-type chain belt for power transmission using the links shown in FIG. caused fatigue failure. The present inventor conducted various experiments and found the following. In other words, the force applied to link 01 when tensile force is applied to the straight part of the V-type chain belt is:
There is only a tensile force F ₁ (Figure 40) from pin 03. At this time, A on the inner circumferential side and the outer circumferential side of the pin hole 02
Stresses F _A and F _B are concentrated at point and point B.
However, the magnitude relationship is F _A ≒ F _B. However, when the V-shaped chain belt is wound around the V-shaped pulley, the force applied to the link 01 is due to the addition of the thrust force F ₂ from the V-shaped block 04 (the 41st
), F _A and F _B at this time become F _A < F _B. Therefore, between point A and point B, point B has more severe stress,
Fatigue fracture occurs starting from point B. Note that one possible solution to this problem is to increase the size of the link shape to ensure a sufficient critical cross-sectional length l. This reduces F _A and F _B and improves stress (increases fatigue strength), but the V-shaped chain belt itself becomes larger and its weight increases, which is not preferable. It is also conceivable to increase the number of links or increase the thickness of the link plate to ensure strength, but this has the same problem. Therefore, in V-type chain belts for power transmission in continuously variable transmissions where space is particularly limited, it is possible to
It is desired that the torque capacity handled by each link be as large as possible. Therefore, an object of the present invention is to improve the fatigue strength of the links in a V-type chain belt for power transmission by reducing the stress on the outer peripheral side of the pin holes without increasing the size of the links.

[Means to solve the problem]

Therefore, the present invention employs the following configuration as a means for solving the above-mentioned problems. That is, the V-type chain belt for power transmission described above is characterized in that the center of the pin hole of the link is offset by a predetermined amount in the inner circumferential direction of the chain with respect to the center of the radial width of the chain. Specifically, FIG. 1, FIG. 2, and FIG. 6 will be described as examples. The V-type chain belt 10 for power transmission includes a plurality of links 20 having pin holes 21 at both ends, and pins that are inserted into the pin holes 21 of the alternately stacked links and connect the links 20 so that they can articulate. 30, and a V-shaped block 50 installed between each pin 30 and having tapered surfaces 51 on both sides that make frictional contact with the V-shaped pulley. The center O of the pin hole 21 of the link 20 is offset by a predetermined amount e in the inner circumferential direction of the chain from the center of the radial width of the chain.

[Effect]

According to the above-mentioned means, since the center O of the pin hole 21 of the link is offset by a predetermined amount e in the inner circumferential direction of the chain with respect to the center of the radial width of the chain,
The critical cross-section length l _B where stress is concentrated in the direction of the outer circumference of the chain in the link 20 and the critical cross-section length l _A where stress is concentrated in the direction of the inner circumference of the chain are expressed as l _B > l _A (l _A + l _B = 2 l).
Therefore, the stress F _B on the outer circumferential side of the chain is reduced compared to the case where l _A = l _B = l as in the conventional link. Therefore, the fatigue strength of the link 20 is improved.

【Example】

Hereinafter, embodiments of the present invention will be described in detail based on the drawings. First, a continuously variable transmission to which the V-type chain belt for power transmission of the present invention shown in FIG. 34 is applied will be described. In the figure, 1 is an input shaft and 2 is an output shaft.
An input pulley (driving pulley) 3 and an output pulley (driven pulley) 4 are connected to the ends of the input shaft 1 and output shaft 2, respectively. The input pulley 3 consists of a fixed pulley 3a provided integrally with the input shaft 1, and a movable pulley 3b fitted on the input shaft 1 so as to be slidable in the axial direction, facing the fixed pulley 3a. ing. A conical surface 5 is formed on the mutually opposing end surfaces, and a circumferential groove (V groove) with a V-shaped cross section is formed between both conical surfaces. Furthermore, an input side piston 3c is press-fitted into the input shaft 1 and fixed in the axial direction by the tightening force (axial force) of a lock nut (not shown), and the outer circumferential surface of this piston 3c is aligned with the inner circumferential surface of the movable pulley 3b. and are fluid-tightly fitted via an O-ring. In this way, the input shaft 1, the movable pulley 3b and the piston 3
A hydraulic chamber 3d is formed by c, and this hydraulic chamber 3
d is connected to an external hydraulic power source through an oil passage 1a formed in the input shaft 1. On the other hand, the output pulley 4 also consists of a fixed pulley 4a and a movable pulley 4b, similar to the case of the input pulley 3, and a conical surface 6 forming a V groove is formed on the opposing surfaces of both pulleys 4a and 4b. . Further, an output side piston 4c is similarly fixed in the axial direction to the output shaft 2, and the outer peripheral surface of the piston 4c is fluid-tightly fitted to the inner peripheral surface of the movable pulley 4b via an O-ring. A hydraulic chamber 4d is formed by the output shaft 2, the movable pulley 4b, and the piston 4c, and is connected to an external hydraulic power source through an oil passage 2a formed in the output shaft 2. A power transmission V-type chain belt (hereinafter referred to as chain belt) 10 is stretched between the input pulley 3 and the output pulley 4. When the width of the V-groove of the input pulley 3 is changed by adjusting the amount of hydraulic oil in the hydraulic chamber 3d of the input pulley 3, the movable pulley 4b of the output pulley 4 follows this and changes its axis. By sliding in the direction, the amount of hydraulic oil in the hydraulic chamber 4d is increased or decreased, and the width changes to match the V-groove of the output pulley 4. That is, by controlling the amount of hydraulic fluid in the hydraulic chamber 3d on the input pulley 3 side, the ratio of the rotational speeds of the input pulley 3 and the output pulley 4, that is, the gear ratio, is changed. Note that the tension of the chain belt 10 is maintained at an optimum value by controlling the oil pressure in the hydraulic chamber 4d of the output pulley 4. [First Embodiment] Next, a V-type chain belt for power transmission according to a first embodiment of the present invention shown in FIGS. 1 to 10 will be described. Fig. 1 is an enlarged front view of the link, Fig. 2 is a side view of Fig. 1, Fig. 3 is an enlarged front view of the roller pin, Fig. 4 is an enlarged front view of the V-shaped block, and Fig. 5 is the side view of Fig. 1.
6 is a perspective view showing a portion of the V-type chain belt; FIG. 7 is a side view of the V-type chain belt, partially shown in cross section;
Fig. 8 is a plan view of Fig. 7, and Fig. 9 is a plan view of Fig. 7.
A cross-sectional view along the line, Fig. 10 is - of Fig. 7.
It is a sectional view along a line. As shown in these figures, the chain belt 10 is roughly divided into an annular chain and a plurality of V-shaped blocks 50. The circular chain has multiple links 2
0, a pin 30 articulating the links 20 with each other, and the links 20 and pin 30
The V-shaped block 50 has tapered surfaces 51 on both sides thereof that make frictional contact with the V-shaped pulleys 3 and 4. The link 20 has a flat plate shape as shown in FIGS. 1 and 2, and has pin holes 2 at both ends.
1 is formed. On both edges surrounding the pin hole 21, protrusions 23 and 24 are provided on the outer and inner circumferential sides in the radial direction of the chain, each having a block receiving surface 22 that contacts a V-shaped block 50, which will be described later. Both protrusions 23 and 24 are separated in the longitudinal direction of the link (left and right direction in FIG. 1).
A block mounting groove 25 is formed between and 24 to which a V-shaped block 50, which will be described later, is mounted. The outer peripheral protrusion 23 and the inner peripheral protrusion 24 are arranged in a plane D that is perpendicular to the longitudinal direction of the link (left-right direction in FIG. 1) and passes through the center O of the pin hole 21.
It is located in a position that includes. This is because when a large torque is applied to a chain belt using links in a normal track shape, cracks occur near the plane passing through the center of the pin holes perpendicular to the longitudinal direction of the links. This is to improve fatigue strength). The outer peripheral protrusion 23 and the inner peripheral protrusion 24 are respectively formed with inclined surfaces 26 and 27 on the sides facing the front and rear V-shaped blocks, and the corners thereof are chamfered in an R shape. (However, the radius is larger on the inner peripheral protrusion 24 side). The chain radial width dimension W in the link body 28 between the block mounting grooves 25 is the chain radial width dimension at the edge of the pin hole.
The relationship W≧W′ is established for W′. Note that the pin hole edge is a portion within radius r. Therefore, the edge width dimension W′ is 2r, in other words W
There is a relationship of ≧2r. Additionally, corners 29 of the block mounting grooves 25 formed between the outer protrusions 23 and the inner protrusions 24 are provided with R to alleviate stress concentration and improve link strength (fatigue strength). is provided. Furthermore, the link 20 can be constructed by offsetting the pin hole 21 by a predetermined amount e in the chain belt inner circumferential direction without changing the external shape of the link. The relationship between the length l _B and the critical cross-section length l _A in the inner peripheral direction of the chain is set to l _B > l _A. In this embodiment, for example, the above l _B =2.4 mm,
l _A = 2.0 mm and l _B / l _A = 1.2. The link 20 can be easily manufactured by punching using a press. Then, a plurality of links 20 having the above-mentioned shape are stacked alternately in the thickness direction, and roller pins 30 are passed through the pin holes 21 of each link to sequentially connect them so that they can articulate with each other, forming an endless shape to form a chain. Configure. Each link 20 is connected to the pin 3 above.
It is preferable that the chain be positioned in the axial direction (chain width direction) with respect to 0. This positioning is performed, for example, by forming annular grooves 31 at both ends of the roller pin 30 as shown in FIG. 3, and attaching E-rings 40 to both annular grooves as shown in FIG. 9. Note that both ends of the roller pin 30 may be caulked. Roller pins 30 protruding from both sides of the chain
A space is provided between the ends of the belt so that they do not come into contact with the front and rear surfaces of the V-shaped block in the belt traveling direction, which will be described later. The length of this roller pin 30 is slightly shorter than the width dimension of the V-shaped block including the adjacent roller pins 30. On the other hand, as shown in FIG. 4, the V-shaped block 50 includes a columnar portion 52 having tapered surfaces 51 on both sides thereof that make frictional contact with the V-groove conical surface 5 of the input pulley and the V-groove conical surface 6 of the output pulley. , and a beam portion 53 spanning both columnar portions, and has a rectangular link hole 54 in the center thereof for accommodating the chain. The chain radial width dimension W of the link hole 54 is set to be substantially the same as the chain radial width dimension of the link body portion 28 . The corner portion of the beam portion 53 forming the link hole 54 is chamfered 55 to avoid interference with the R portion of the block mounting groove corner portion 29 of the link 20. Further, the front surface 56 and rear surface 57 of the V-shaped block 50 in the belt traveling direction are smooth surfaces that are parallel to each other, and the V-shaped block plate thickness dimension _t1 shown in FIG. 5 is approximately the same as the width dimension of the block mounting groove 25. It is set. The power transmission V-type chain belt 10 having the above structure can be assembled as follows. First, a plurality of links 20 are obliquely inserted into the link holes 54 of the V-shaped block, and the links 20 are rotated and assembled to a proper position where the block mounting grooves 25 and the link holes 54 engage. Next, the links 20 are stacked in the thickness direction by shifting every other link in the longitudinal direction of the chain, and the roller pins 30 are inserted into the pin holes 21 of each link.
E-links 40 are attached to 1 and sequentially connected to each other so as to be able to move in articulation. This operation is repeated one after another to construct the endless chain belt 10 shown in FIGS. 6 to 8. In FIG. 7, T _P indicates the chain pitch (distance between the centers of a pair of pins), and P-P indicates the pitch line. In the assembled state, the V-shaped block 5
0 does not contact the roller pin 30 but engages with the block mounting groove 25 of the link 20, as shown in FIG. The front surface 56 and rear surface 57 of the chain are brought into contact with the block receiving surface 22 and positioned in the longitudinal direction of the chain. On the other hand, in the chain width direction, it is desirable that the chain and the V-shaped block 50 be arranged with a gap between them so that they can slide relative to each other, taking into account misalignment between the input and output pulleys. That is, a distance C/2 is provided between both side surfaces of the link 20 (both side surfaces of the chain) facing each other and the link hole end surface 58 of the V-shaped block. The total distance C is set to be larger than the maximum misalignment amount δ between the input pulley 3 and the output pulley 4 that occurs in the continuously variable transmission (see FIG. 35). In other words, the relationship is C>δ. In the V-shaped chain belt 10 for power transmission configured as described above, the clamping force from the V-shaped pulley due to the hydraulic thrust acting on the back surfaces of the input pulley 3 and the output pulley 4 is borne by the V-shaped block 50. . In this state, the rotational power from the input pulley 3 is applied to the V-shaped block 50 which is in frictional contact in the V-groove.
It is transmitted to The power transmitted to the V-shaped block 50 is transmitted to each link 20 and roller pin 30, and then sequentially transmitted to the rear V-shaped block 50. At this time, the rear V-shaped block 50 is directly pulled by the protrusions 23 and 24 of each link,
Generates tensile force on the chain. In this way, the protrusions 23 and 24 of each link 20 and the roller pin 3
0, power is transmitted to the output pulley 4 via the V-shaped block 50 using the same theory as a rubber belt. Now, in this embodiment, the critical section lengths of the link 20 in the chain outer circumferential direction and the chain inner circumferential direction are set to the relationship l _B > l _A (l _A +l _B = 2l), so that the conventional link As compared to the case where l _A =l _B =l, the stress at point B, where the stress is most severe, that is, the stress F _B in the chain outer circumferential direction is reduced. As a result, l _B / l _A = 1.2 (l _B = 2.4 mm, l _A = 2.0 mm)
The fatigue strength of the V-type chain belt 10 for power transmission according to this embodiment, which is set to l _B /l _A = 1 (l _A = l _B =
2.2 mm), this is an improvement of approximately 5 to 10%, as shown in Figure 11. Note that fatigue strength is improved by setting l _B /l _A to 1.5 or less. However, in the range of l _B /l _A >1.5, the stress at point A becomes severe (l _A → small, F _A → increases), and the link fatigue strength decreases. Therefore, l _B /l _A =about 1.2 is particularly preferred. Therefore, according to this embodiment, the fatigue strength of the link 20 can be greatly improved without increasing the size, and the V-type chain belt 1 for power transmission can be improved.
It is possible to improve the durability of 0. In addition, the outer circumference side protrusion 23 and the inner circumference side protrusion 2
4 is provided at a position that includes the plane D passing through the pin hole center O that is perpendicular to the longitudinal direction of the link, so that the link strength (fatigue strength) is improved. Furthermore, since the chain radial width dimension W in the link body 28 between the block mounting grooves 25 is set to the relationship W≧W' with respect to the chain radial width dimension W' at the edge of the pin hole 21, the link Strength (fatigue strength) can be further improved. In other words, when tension is applied to the chain, the link 20 is
When it is pulled at 0, the tension is mostly shared by the portion inside the width dimension W' at the edge of the pin hole. Therefore, the block mounting groove 25 and its corner 29 are
The strength of the link varies greatly depending on whether or not it is within the range of the width W' of the edge of the pin hole. Therefore, the third
The link strength is greater than that of the conventional link shape shown in FIG. Furthermore, since the block mounting groove corner 29 of the link 20 is rounded, the corner 2
The stress concentration occurring at 9 is alleviated. Since the strength of the link 20 has been improved in this way, the torque capacity per pair of links can be greatly increased, making it ideal as a chain belt for a continuously variable transmission where space is extremely limited. Further, the V-shaped block 50 has a protruding portion 2 of each link.
3 and 24, the contact area between them is large and a large torque can be transmitted. In addition, the link 20 and the V-shaped block 50
Since there is little sliding between the parts, the transmission efficiency is good, and there is little wear and tear, resulting in excellent durability. Therefore, it is compact as a chain belt for transmitting large torque, and it is possible to reduce weight and cost. Furthermore, in a belt-type continuously variable transmission that has an extremely wide speed change range, such as that used in automobiles, when in use, as shown in FIG. A so-called misalignment occurs in which the groove center plane F deviates by δ in the axial direction. If this misalignment occurs, the belt 10 will be caught in the input pulley 3 and the output pulley 4 in a twisted state, which will deteriorate the durability of the belt 10. In particular, in the case of the chain belt 10, each link has high rigidity, and the amount of movement in the chain width direction between the V-shaped block and the chain is regulated to be extremely small in terms of vibration and noise. It is not possible to absorb the misalignment that occurs between the two. Therefore, as shown in FIG. 35, each link is twisted relative to the V-shaped block, and there is a risk that each link may be worn out or even damaged. However, according to this embodiment, even if misalignment occurs between the input and output pulleys 3 and 4, the V-shaped block 50 can be moved in the lateral direction (width direction) with respect to the chain. Misalignment can be easily absorbed. As a result,
The chain is always kept in a straight state, and no abnormal stress is applied to the chain, greatly improving the fatigue durability of the chain. [Second Embodiment] Figures 12 to 17 show a V-type chain belt for power transmission according to a second embodiment of the present invention.
The figure is a side view of the V-shaped chain belt, partially shown in cross section, Figure 13 is a sectional view taken along the - line in Figure 12, Figure 14 is an enlarged front view of the link, and Figure 15 is the body part. Vertical cross-sectional view of the link cut at
FIG. 16 is an enlarged front view of the V-shaped block, and FIG. 17 is a sectional view taken along the line - in FIG. 16. In addition, in FIGS. 12 to 17, the first
Figures 2, 4, 5, 7 and 9
Portions corresponding to the figures are given the same reference numerals as those in these figures, and detailed explanation thereof will be omitted. In this embodiment, the shape of the corner of the block mounting groove in the link is changed so that a V-shaped block without chamfering on the beam can be used. That is, as shown in FIGS. 14 and 15, the corner 29 of the block mounting groove 25 formed between the outer protrusions 23 and the inner protrusions 24 provided on the link 20 has an R-shaped corner 29. An escape groove 29a is provided. This R-shaped relief groove 29a is provided not in the chain radial direction but in the link longitudinal direction. Further, the link 20 can be constructed by offsetting the pin hole 21 by a predetermined amount in the chain inner circumferential direction without changing the external shape of the link, as in the previous embodiment, so that the link 20 can be moved from the pin hole 21 in the chain outer circumferential direction as shown in FIG. The relationship between the dangerous section length l _B and the dangerous section length l _A in the inner circumferential direction of the chain is set as l _B > l _A. On the other hand, in the V-shaped block 50, the corners of the beam portions 53 are not chamfered, as shown in FIGS. 16 and 17. When the link 20 is assembled to the V-shaped block 50, the R-shaped relief groove 29a prevents interference between the corner of the V-shaped block 50 and the block mounting groove corner 29 of the link 20, as shown in FIG. be done. Therefore, in this embodiment, there is no need to chamfer the beam portion 53 of the V-shaped block, and manufacturing costs can be reduced. Further, since the R-shaped relief groove 29a is provided along the longitudinal direction of the link (the longitudinal direction of the chain), there is almost no reduction in link strength compared to the case where the R-shaped relief groove is provided in the radial direction of the chain. [Third Embodiment] Figures 18 to 27 show a V-type chain belt for power transmission according to a third embodiment of the present invention.
The figure is a perspective view of a part of the V-type chain belt (however, the pin holder is removed for ease of understanding), and Figure 19 is a partial cross-section of the V-type chain belt. A side view of the belt, Fig. 20 is a plan view of Fig. 19, Fig. 21 is a sectional view taken along the - line of Fig. 19, Fig. 22 is an enlarged front view of the link, and Fig. 23 is an enlarged perspective view of the rocker pin. Figure 24 is an enlarged front view of the V-shaped block, Figure 25 is a side view of Figure 24, Figure 26 and
Figure 7 is an enlarged front view and side view of the pin holder. In addition, in FIGS. 18 to 25, the parts corresponding to the drawings of the second embodiment are designated by the same reference numerals as in those figures, and detailed explanation thereof will be omitted. In this embodiment, a rocker pin 35 having excellent wear resistance is used in place of the roller pin 30 that connects the links 20 so as to be able to articulate with each other. That is, as shown in FIG. 22, the pin hole 21 formed in the link 20 is not a perfect circle but has a circular arc-shaped detent projection 21a. Further, the link 20 is constructed by offsetting the pin hole 21 by a predetermined amount in the chain inner circumferential direction without changing the external shape of the link, as in the previous embodiment, so that the link 20 can be offset from the pin hole 21 in the chain outer circumferential direction as shown in FIG. The relationship between the dangerous section length l _B and the dangerous section length l _A in the inner circumferential direction of the chain is set as l _B > l _A. On the other hand, the rocker pin 35 has a curved cross section as shown in FIG. 23, and has a locking recess 35a on its inner periphery that engages with the locking projection 21a of the link, and a part of a cylindrical surface on its outer periphery. It has a rolling surface 35b and a fixed surface 35c that engages with the inner peripheral surface of the pin hole 21 of the link. In addition, the V-shaped block 50 has a link hole 54a having a rectangular shape as shown in FIG. It is formed on a thin curved surface 53a. Further, the V-shaped blocks 50 are used in pairs. In other words, the thickness of one plate of the V-shaped block 50 is set to half the plate thickness t ₁ /2 of the second embodiment, as shown in FIG. As in the example, there is no chamfering. Furthermore, a pin holder 60 (second
6 and 27) are used. This pin holder 60 is formed from a spring steel plate, has a curved base 61, and has legs 6 bent on both sides of the base.
2, and a claw portion 63 with the tip of the leg portion folded back into a U-shape. In the free state, the dimension G ₂ between the pair of opposing pawls 63 is set smaller than the chain width dimension G ₁ shown in FIG. 21. Further, the dimension H ₂ between the inner surface of the curved base 61 and the tip of the claw portion 63 is determined by the link 2 shown in FIG.
This is set smaller than the dimension H ₁ between the outer peripheral end surface of the rocker pin 35 and the inner peripheral end surface of the rocker pin 35 . Note that the width dimension t ₂ (Fig. 27) of the pin holder 60 is as follows:
Even when the chain belt is in the straight state shown in Fig. 19 and wrapped around the pulley, the front and rear V-shaped blocks 50
The dimensions are set in advance so as not to interfere with the The power transmission V-type chain belt 10 having the above structure can be assembled as follows. First, the link 20 is inserted diagonally into the link hole 54 of a set of two V-shaped blocks 50, and the block mounting groove 25 is inserted while rotating the link 20.
and the link hole 54 are assembled in a proper position where they engage with each other. Next, the links 20 are stacked in the thickness direction by shifting every other link in the longitudinal direction of the chain, and a pair of rocker pins 35 are placed back to back in the pin hole 21 of each link so that the rolling surfaces 35b are in contact with each other. insert. Furthermore, the pin holder 60 is assembled from above using its spring action. In this state, the curved base 61 of the pin holder contacts the outer circumferential end surface of the link 20, the claw portion 63 at the tip of the leg is pressed against the link side surface and the rocker pin 35, and is reliably positioned and held by the action of the spring. Note that a predetermined gap is formed between the inner surface of the leg portion 62 of the pin holder and the end surface of the rocker pin 35. This operation is repeated one after another to construct an endless chain belt 10. Note that the pin holder 6
0, by lengthening one of the set of rocker pins 35 and attaching a snap link to a groove formed at the end of the link 2.
0 and the rocker pin 35 may be positioned in the chain width direction. According to this embodiment, the vibration noise of the chain belt 10 can be reduced, and the chain belt 10
elongation of the chain belt 10 can be suppressed, which in turn leads to an improvement in the life of the chain belt 10. [Fourth Embodiment] FIGS. 28 and 29 show a V-type chain belt for power transmission according to a fourth embodiment of the present invention, and FIG. 28 shows a V-type chain belt partially shown in cross section. A side view of the belt, and FIG. 29 is an enlarged front view of the link. Note that in FIGS. 28 and 29, parts corresponding to those of the third embodiment are designated by the same reference numerals as in these figures, and detailed explanation thereof will be omitted. In this embodiment, in the V-type chain belt for power transmission according to the third embodiment, a bending prevention surface is provided on the outer circumferential side protrusion of the link to reduce noise caused by resonance phenomenon particularly in the straight portion of the chain belt. It is something like that. That is, the outer circumferential protrusion 23 of the link is formed with a bending prevention surface 26a that can come into contact with the front and rear V-shaped blocks, respectively. This bending prevention surface 26
a is formed. This bending prevention surface 26a is
They are each formed parallel to the block receiving surface 22 of the protrusion. The link longitudinal width dimension t ₂ of the outer circumferential protrusion 23 is based on the chain pitch t _p (distance between the centers of a pair of pins) and the plate thickness t ₁ of the pair of V-shaped blocks shown in FIG. Therefore, t ₂ ≦t _p −
The relationship is set to t ₁ . By the way, in the case of the chain belts described in the above-mentioned Japanese Utility Model Publication No. 39-3919 and Publication Utility Model Publication No. 40-13929, the chain belt 10 has an inner circumferential side and an outer circumferential side, as shown by the two-dot chain line in FIG. It can be bent freely on both sides. For this reason, when the chain belt 10 is stretched around the input pulley 3 and the output pulley 4, deflection occurs due to its own weight, and under certain rotation conditions, the straight portion 10s of the chain belt 10 causes a resonance phenomenon. Therefore, due to the resonance phenomenon, impact force is repeatedly applied to the chain belt 10 itself, which may increase noise and deteriorate durability. However, according to this embodiment, since the bending preventing surface 26a is formed on the outer peripheral side protrusion 23 of each link, one bending preventing surface 26a comes into contact with the front V-shaped block rear surface 57, and the other bending preventing surface 26a comes into contact with the front V-shaped block rear surface 57. 26
a comes into contact with the rear V-shaped block front surface 56, and the chain belt 10 is prevented from bending inward.
Note that the bending preventing surface 26a does not necessarily have to be formed parallel to the block receiving surface 22, and the angle between the bending preventing surface 26a and the outer peripheral end surface of the link is set to be smaller than the angle between the inclined surface 27 and the inner peripheral end surface of the link. It may also be set on a large slope. Therefore, according to this embodiment, even if the chain belt 10 is stretched around the input pulley 3 and the output pulley 4 in a horizontal state, there is almost no deflection due to its own weight.
The resonance phenomenon occurring in the straight portion of the chain belt 10 is suppressed. As a result, the noise caused by the resonance phenomenon in the chain belt straight portion can be significantly reduced, and the chain belt 10
The durability can be improved. [Fifth Embodiment] Next, FIGS. 30 to 33 show a V-type chain belt for power transmission according to a fifth embodiment of the present invention, and FIG. 30 shows a part in cross section. A side view of the V-type chain belt, Figure 31 is similar to Figure 30.
32 is an enlarged front view of the link, and FIG. 33 is a side view of FIG. 32. Note that in FIGS. 30 to 33, parts corresponding to the drawings of the third embodiment are designated by the same reference numerals as in these figures, and detailed explanation thereof will be omitted. This embodiment differs from the chain belt of the first embodiment shown in Figs. It is provided only at the edges. That is, the chain belt 100 includes the links 200 shown in FIGS. 32 and 33, and the
It is composed of a rocker pin 30 having the same shape as shown in the figure, a V-shaped block 50 having the same shape as shown in FIGS. 24 and 25, and a pin holder 60 having the same shape as shown in FIGS. 26 and 27. The link 200 has a flat plate shape as shown in FIGS. 32 and 33, and has a pin hole 210 with arc-shaped detent projections 211 at both ends thereof.
is formed. One edge surrounding the pin hole 210 is provided with protrusions 230 and 240 having block receiving surfaces 220 on the outer and inner circumferential sides in the radial direction of the chain for contacting V-shaped blocks to be described later. The outer circumferential side protrusion 230 and the inner circumferential side protrusion 240 are arranged in the longitudinal direction of the link (the third
2), and the pin hole 2
It is provided at a position that includes a plane D passing through the center O of 10. The outer peripheral protrusion 230 and the inner peripheral protrusion 240 are respectively formed with inclined surfaces 260 and 270 on the sides facing the front and rear V-shaped blocks. Additionally, an R-shaped relief groove 290 is provided at the corner between the block receiving surface 220 and the link body 280 along the link longitudinal direction in order to alleviate stress concentration and improve link strength (fatigue strength). It is formed. Furthermore, regarding the link 200 as well, the pin hole 21 can be fixed without changing the outer shape of the link as in the above embodiment.
By offsetting 0 by a predetermined amount in the direction of the inner circumference of the chain, the relationship between the critical cross-sectional length l _B in the outer circumferential direction of the chain from the pin hole 210 and the dangerous cross-sectional length l _A in the inner circumferential direction of the chain as shown in FIG. , l _B > l _A is set. The V-type chain belt 100 for power transmission having the above configuration can be assembled in the following manner. First, a plurality of links 200 are inserted into the link hole 54 from the front side 56 and rear side 57 of the V-shaped block so that the block receiving surfaces 220 of the protruding portions are positioned alternately on the left and right sides. Next, the rocker pins 35 are inserted into the pin holes 210 of each link with their backs facing each other so that their rolling surfaces 35b are in contact with each other. Furthermore, the pin holder 6
0 from above the chain using its spring force. This operation is repeated one after another to construct an endless chain belt 100. In this way, the chain belt 100 can be assembled extremely easily. In the assembled state, the V-shaped block 5
0 is a block receiving surface 220 whose front surface 56 is formed on one link 200, and a block receiving surface 220 whose rear surface 57 is formed on the other link 200.
and is positioned in the longitudinal direction of the chain. On the other hand, in the chain width direction, the chain and the V-shaped block 50 are arranged with a gap between them so that they can be slid relative to each other in consideration of misalignment between the input and output pulleys. Also in the V-type chain belt 100 for power transmission configured as described above, the rotational power from the input pulley 3 is transmitted from the V-type block 50 to each link 200 to the rocker pin 35, as in each of the embodiments described above.
→It is sequentially transmitted to the rear V-shaped block 50 via each link 200. At this time, the rear V-shaped block 50 is directly pulled by the protrusions 230 and 240 of each link, creating a tensile force in the chain. Thus, the protrusions 230, 240 of each link
and the V-shaped block 5 through the rocker pin 30.
Power is transmitted to the output pulley 4 via the rubber belt according to the same theory as the rubber belt. Therefore, according to this embodiment, it is possible to obtain the same effects as those of the above-mentioned embodiments, and it is also easy to insert each link 200 into the V-shaped block link hole 54, making it easier to assemble the chain belt 100. Workability is extremely good. Although not shown, a bending prevention surface may be formed on the outer peripheral protrusion 230 of the link 200 in the same configuration as in the fourth embodiment (FIGS. 28 and 29). Although the present invention has been described above with reference to specific embodiments, the present invention is not limited to the above-mentioned embodiments, but includes various embodiments within the scope of the claims for utility model registration. Yes, for example, dividing a V-shaped block into two in the chain width direction,
The two may be integrated by a connecting means such as a connecting pin, a rivet, or a bolt/nut. In addition, it is possible to combine each embodiment, and
Modifications of the links, pins, and V-block components are also possible.

[Effect of the idea]

As described above, according to the present invention, in a V-type chain belt for power transmission, the stress on the outer peripheral side of the pin hole can be reduced without increasing the size of the link, and the fatigue strength of the link can be improved. Therefore, the durability of the V-type chain belt can be greatly improved.

[Brief explanation of the drawing]

1 to 10 show a V-type chain belt for power transmission according to the first embodiment of the present invention, FIG. 1 is an enlarged front view of the link, and FIG. 2 is an enlarged front view of the link.
Figure 3 is a side view, Figure 3 is an enlarged front view of the roller pin,
Fig. 4 is an enlarged front view of the V-shaped block, Fig. 5 is a sectional view taken along the - line in Fig. 4, Fig. 6 is a perspective view showing a part of the V-shaped chain belt, and Fig. 7 is a cross-sectional view of the V-shaped chain belt. 8 is a plan view of FIG. 7, FIG. 9 is a sectional view taken along the - line of FIG. 7, and FIG. 11 is a graph showing the relationship between the ratio of the critical cross-sectional length from the pin hole in the link in the direction of the outer circumference of the chain and the direction of the inner circumference of the chain and the fatigue strength of the link, Fig. 12 to 17 12 shows a V-type chain belt for power transmission according to a second embodiment of the present invention, FIG. 12 is a side view of the V-type chain belt partially shown in cross section, and FIG. 1st cross-sectional view along the - line of
Figure 4 is an enlarged front view of the link, Figure 15 is a vertical sectional view of the link cut at the body, Figure 16 is an enlarged front view of the V-shaped block, and Figure 17 is a view taken along the - line in Figure 16. The sectional views, FIGS. 18 to 27, show a V-type chain belt for power transmission according to a third embodiment of the present invention, and FIG. 18 is a perspective view showing a part of the V-type chain belt. Fig. 19 is a side view of the V-type chain belt partially shown in cross section, Fig. 20 is a plan view of Fig. 19, Fig. 21 is a sectional view taken along line XI-XI of Fig. 19, Fig. 22 is an enlarged front view of the link, Fig. 23 is an enlarged perspective view of the rocker pin, Fig. 24 is an enlarged front view of the V-shaped block, Fig. 25 is a side view of Fig. 24, and Fig. 26 is an enlarged front view of the pin holder. 27 is a side view of FIG. 26, and FIGS. 28 and 29 are the fourth views of the present invention.
28 is a side view of the V-type chain belt partially shown in cross section, FIG. 29 is an enlarged front view of the link, and FIG. 30 shows a V-type chain belt for power transmission according to an embodiment. 33 shows a V-type chain belt for power transmission according to a fifth embodiment of the present invention, FIG. 30 is a side view of the V-type chain belt partially shown in cross section, and FIG. 31 is the third
Cross-sectional view along the XI-XI line of Figure 0, No. 32
The figure is an enlarged front view of the link, Figure 33 is a side view of Figure 32, and Figure 34 is a vertical sectional view of essential parts showing an example of a continuously variable transmission to which the V-type chain belt for power transmission of the present invention is applied. , Fig. 35 is a schematic external view showing a state where misalignment has occurred between both pulleys in a continuously variable transmission using a V-belt for power transmission, and Figs. 36 to 3
Figure 9 shows a conventional V-type chain belt for power transmission, Figure 36 is a side view of the V-type chain belt, and Figure 37 is a side view of the V-type chain belt in Figure 36.
38 is an enlarged front view of the link, FIG. 39 is a side view of FIG. 38, FIGS. 40 and 41 are comparative examples of the link, and FIG. 40 is an enlarged front view of the link. FIG. 41 is an enlarged front view showing the force relationship acting on the links in the straight portion of the V-type chain belt; FIG. FIG. 42 is a schematic diagram showing a state in which a resonance phenomenon occurs in a continuously variable transmission using a conventional V-type chain belt for power transmission. Explanation of symbols, 3...Input pulley (V-type pulley),
4...Output pulley (V-type pulley), 10,100
...V-type chain belt for power transmission, 20,20
0... Link, 21, 210... Pin hole, 22,
220...Block receiving surface, 23, 230...Outer circumference side protrusion, 24,240...Inner circumference side protrusion, 2
5...Block mounting groove, 26,260...Slanted surface on the outer peripheral side, 26a...Bending prevention surface, 27,270
... Inner peripheral side slope, 28, 280 ... Link body, 29 ... Corner, 29a, 290 ... R-shaped relief groove, 30 ... Roller pin (pin), 35 ...
Rotsukar pin (pin), 40...E ring, 50
... V-shaped block, 51 ... Tapered surface, 54 ...
Link hole, 55... Chamfering, l _A ... Hazardous cross section length from the link pin hole to the outer circumference of the chain, l _B ... Hazardous cross section length from the link pin hole to the inner circumferential direction of the chain.

Claims (1)

[Scope of claims for utility model registration] (1) A plurality of links having pin holes at both ends,
An annular chain consisting of pins that are inserted into the pin holes of alternately stacked links and connect the links so that they can move together; and a tapered surface that is installed between each pin and makes frictional contact with the V-shaped pulley on both sides. A V-shaped chain belt for power transmission comprising a V-shaped block having a V-shaped block, characterized in that the center of the pin hole of the link is offset by a predetermined amount in the inner circumferential direction of the chain with respect to the center of the radial width of the chain. A V-type chain belt for power transmission. (2) The offset amount of the center of the pin hole is determined by the relationship between the critical cross-sectional length l _B where stress is concentrated from the pin hole of the link in the direction of the outer circumference of the chain, and the critical cross-sectional length l _A where stress is concentrated in the direction of the inner circumference of the chain. The V-type chain belt for power transmission according to claim 1, wherein l _B is set to be larger than l _A and l _B /l _A is 1.5 or less. (3) The link is provided with protrusions having block receiving surfaces on the outer and inner circumferential sides in the chain radial direction from both edges surrounding the pin hole, and both protrusions separated in the longitudinal direction of the link. The V-shaped chain belt for power transmission according to claim 1, wherein the V-shaped block is attached to a block attachment groove formed between the belts. (4) The link is provided with a protrusion having block receiving surfaces on the outer and inner circumferential sides in the chain radial direction from one edge surrounding the pin hole, and each link is provided with a block receiving surface on the protruding part. The power unit according to claim 1 of the utility model registration claim, characterized in that the power unit is inserted into a link hole formed in the center of the V-shaped block so that the left and right surfaces are alternately located, and connected by the pin. Transmission V
Type chain belt. (5) The outer protrusion and the inner protrusion are provided at positions including a plane passing through the center of the pin hole orthogonal to the longitudinal direction of the link. Section 3 or Section 4
V-type chain belt for power transmission as described in section. (6) The chain radial width dimension W of the link body to which the V-shaped block is attached is relative to the chain radial width dimension W' of the pin hole edge.
The V-type chain belt for power transmission according to claim 3 or 4, characterized in that the relationship W≧W′ is established. (7) A utility model registration characterized in that a radius is provided at the corner of the block receiving surface of the outer circumference side protrusion part and the inner circumference side protrusion part and the link body part to which the V-shaped block is attached. A V-type chain belt for power transmission according to claim 3 or 4. (8) R-shaped relief grooves are provided in the longitudinal direction of the link at the corners of the block receiving surfaces of the outer circumference side protrusion and the inner circumference side protrusion and the link body to which the V-shaped block is attached. A V-type chain belt for power transmission according to claim 3 or 4 of the utility model registration claim. (9) The power transmission according to claim 3 or 4 of the utility model registration claim, wherein the outer circumferential side protrusion is provided with a bending prevention surface that can come into contact with the front and rear V-shaped blocks, respectively. V-type chain belt for use. (10) The V-type chain belt for power transmission according to claim 9, wherein the bending prevention surface of the outer circumferential protrusion is formed substantially parallel to the block receiving surface. (11) Link longitudinal width dimension t ₂ of the outer peripheral protrusion
are chain pitch _tp and V-type block plate thickness dimensions
Utility model registration claim No. ₁ characterized in that the relationship t ₂ ≦ t _p − _{t 1} is established for t 1.
V-type chain belt for power transmission as described in item 10. (12) The V for power transmission according to claim 1, wherein the link is positioned with respect to the pin in its axial direction.
Type chain belt. (13) The V-type chain belt for power transmission according to claim 1, wherein the pin is a roller pin. (14) The V-type chain belt for power transmission according to claim 1, wherein the pin is a Rocker pin. (15) The V-shaped block has a link hole in the center, and a gap larger than the maximum misalignment between the V-shaped pulleys is provided between the end surface of the link hole and the opposing side surface of the link. The V-type chain belt for power transmission according to claim 1 of the utility model registration claim, characterized in that: