JP4411532B2 - Power transmission chain and power transmission device including the same - Google Patents

Description

  The present invention relates to a power transmission chain and a power transmission device including the power transmission chain.

In an endless power transmission chain used in a power transmission device such as a pulley-type continuously variable transmission (CVT), a plurality of links, pins that connect adjacent links to each other, and each link are inserted. Some include a sliding member formed of a set of two round bars (see, for example, Patent Document 1). The two round bars are pressed against a pulley having a pair of conical surfaces, whereby power is transmitted between the power transmission chain and the pulley.
Japanese Utility Model Publication No. 3-84459

  Conventionally, there has been a demand for further noise reduction in power transmission chains used in power transmission devices such as CVT. Then, an object of this invention is to provide a power transmission chain which can solve said subject, and a power transmission device provided with the same.

The inventor of the present application provides a pair of power transmission members in a power transmission chain having a power transmission member in contact with the pulley, and sets the contact state between each of the pair of power transmission members and the pulley to a predetermined state. However, the present invention has been conceived with the knowledge that it is effective in reducing noise during driving of the power transmission chain.
Specifically, the present invention includes a plurality of links, and first and second power transmission members that connect these links to each other and are in rolling contact with each other, and the first power transmission member is a pulley. In the power transmission chain that is sandwiched between a pair of opposed sheave surfaces and transmits power between the first power transmission member and the pulley, the second power transmission member is a first power transmission in a free state. The pair of end portions of the second power transmission member make light contact with the corresponding sheave surfaces in a state where the first power transmission member is sandwiched between the pair of sheave surfaces and is elastically contracted. In this way, it is characterized by that.

  According to the present invention, power can be transmitted between the power transmission chain and the pulley by holding the first power transmission member between the pulleys. Further, when the first power transmission member is engaged with the pulley, each of the pair of end portions of the second power transmission member is lightly brought into contact with the corresponding sheave surface of the pulley, whereby the second power transmission member Is moderately restrained by the sheave surface, the occurrence of vibration of the second power transmission member can be prevented in advance, and the noise during driving of the chain can be significantly reduced.

  Further, in the present invention, when the end portion of the second power transmission member makes light contact with the corresponding sheave surface, the pressing force received from the corresponding sheave surface by the end portion of the second power transmission member is the first The end of the power transmission member may be 0 to 80% of the maximum pressing force received from the corresponding sheave surface. In this case, since the pressing force received by the second power transmission member is 0% or more of the maximum pressing force received by the first power transmission member, the occurrence of vibration of the second power transmission member is reliably prevented. be able to. In addition, since the pressing force received by the second power transmission member is 80% or less of the maximum pressing force received by the first power transmission member, the second power transmission member is excessively pressed by the pulley, and the torcross is It can be prevented from increasing.

  In the present invention, the difference between the length of the first power transmission member in the free state and the length of the second power transmission member is 20 to 100% of the maximum elastic contraction amount of the first power transmission member. There is a case. In this case, since the difference is 20% or more of the maximum elastic contraction amount of the first power transmission member, it is possible to prevent the second power transmission member from being excessively pressed by the pulley and increasing the torque cross. In addition, since the difference is set to 100% or less of the maximum elastic contraction amount of the first power transmission member, the second power transmission member and the pulley can reliably achieve a light contact, and the second power transmission Generation of vibration of the member can be reliably prevented.

  In the present invention, the difference between the length of the first power transmission member in the free state and the length of the second power transmission member may be 5 to 50 μm. In this case, since the difference is 5 μm or more, it is possible to prevent the second power transmission member from being excessively pressed by the pulley and increasing the torque cross. In addition, since the difference is 50 μm or less, it is possible to reliably achieve light contact between the second power transmission member and the pulley, and to reliably prevent occurrence of vibration of the second power transmission member.

  In the present invention, the first and second pulleys each having a pair of conical sheave surfaces facing each other, and the pulleys wound around the pulleys and engaged with the sheave surfaces to transmit power. The power transmission chain may be provided. In this case, a power transmission device excellent in silence can be realized.

Preferred embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 schematically shows a main configuration of a chain-type continuously variable transmission (hereinafter also simply referred to as a continuously variable transmission) as a power transmission device including a power transmission chain according to an embodiment of the present invention. It is a perspective view. Referring to FIG. 1, a continuously variable transmission 100 is mounted on a vehicle such as an automobile, and includes a drive pulley 60 made of metal (such as structural steel) as a first pulley, and a second pulley. And a driven pulley 70 made of metal (such as structural steel) and an endless power transmission chain 1 (hereinafter also simply referred to as a chain) wound between the pulleys 60 and 70. . In addition, the chain 1 in FIG. 1 has shown a partial cross section for easy understanding.

  FIG. 2 is a partially enlarged sectional view of the drive pulley 60 (driven pulley 70) and the chain 1 of FIG. Referring to FIGS. 1 and 2, drive pulley 60 is attached to an input shaft 61 that is connected to a vehicle drive source so that power can be transmitted, and includes a fixed sheave 62 and a movable sheave 63. The fixed sheave 62 and the movable sheave 63 have a pair of sheave surfaces 62a and 63a that face each other. The sheave surfaces 62a and 63a include conical inclined surfaces. A groove is defined between the sheave surfaces 62a and 63a, and the chain 1 is held between the grooves 1 with a strong pressure.

  The movable sheave 63 is connected to a hydraulic actuator (not shown) for changing the groove width, and moves the movable sheave 63 in the axial direction of the input shaft 61 (left and right in FIG. 2) during shifting. By doing so, the groove width is changed. Thereby, the chain 1 is moved in the radial direction of the input shaft 61 (vertical direction in FIG. 2), and the winding radius R of the chain 1 around the input shaft 61 (pulley 60) (effective radius R with respect to the first pin 3). Can be changed.

  On the other hand, as shown in FIGS. 1 and 2, the driven pulley 70 is attached to an output shaft 71 that is connected to a drive wheel (not shown) so as to be capable of transmitting power and is integrally rotatable. A fixed sheave 72 and a movable sheave 73 having a pair of opposed sheave surfaces 72a and 73a for forming a groove for sandwiching the chain 1 with high pressure are provided. A hydraulic actuator (not shown) is connected to the movable sheave 73 of the driven pulley 70 similarly to the movable sheave 63 of the drive pulley 60, and the groove width is changed by moving the movable sheave 73 during shifting. It is like that. As a result, the chain 1 can be moved to change the winding radius R of the chain 1 around the output shaft 71 (pulley 70).

FIG. 3 is a perspective view schematically showing the configuration of the main part of the chain 1. 4 is a cross-sectional plan view of the main part of the chain shown in FIG. FIG. 5 is a cross-sectional view taken along the line II-II in FIG. 4 and shows a chain straight line portion.
3 and 4, chain 1 includes a plurality of links 2 and a plurality of first and second pins 3 and 4 as first and second power transmission members that are in rolling contact with each other. It has. The rolling sliding contact means a contact including at least one of a rolling contact and a sliding contact.

Referring to FIGS. 4 and 5, each link 2 is formed in a plate shape and includes a front end portion 7 and a rear end portion 8 as a pair of end portions arranged in the front and rear in the chain traveling direction X. A front through hole 9 and a rear through hole 10 are formed in the front end portion 7 and the rear end portion 8, respectively.
First to third columns 51 to 53 are formed using the link 2. Specifically, each of the first row 51, the second row 52, and the third row 53 includes a plurality of links 2 arranged in the chain width direction W. In each of the first to third rows 51 to 53, the links 2 in the same row are aligned so that the positions in the chain traveling direction X are the same. The first to third rows 51 to 53 are arranged along the chain traveling direction X.

The links 2 in the first to third rows 51 to 53 are respectively connected to the links 2 in the corresponding first to third rows 51 to 53 using the corresponding first and second pins 3 and 4. It is connected so that it can be bent.
Specifically, the front through hole 9 of the link 2 in the first row 51 and the rear through hole 10 of the link 2 in the second row 52 correspond to each other in the chain width direction W. The links 2 of the first and second rows 51 and 52 are connected to each other so as to be bendable in the chain traveling direction X by first and second pins 3 and 4 that pass through the through holes 9 and 10.

Similarly, the front through hole 9 of the link 2 in the second row 52 and the rear through hole 10 of the link 2 in the third row 53 correspond to each other in the chain width direction W. The links 2 in the second and third rows 52 and 53 are connected to each other so as to be able to bend in the chain traveling direction X by the first and second pins 3 and 4 inserted through the holes 9 and 10.
In FIG. 4, only one of the first to third columns 51 to 53 is shown, but the first to third columns 51 to 53 are arranged so as to repeat along the chain traveling direction X. Yes. The links 2 in two rows adjacent to each other in the chain traveling direction X are sequentially connected by corresponding first and second pins 3 and 4 to form an endless chain 1.

The first pin 3 is a rod-like body extending in the chain width direction W. The pair of end portions 15 and 16 of the first pin 3 protrude in the chain width direction W from the links 2 arranged at the pair of end portions in the chain width direction W, respectively. The pair of end portions 15 and 16 of the first pin 3 are provided with power transmission portions 5 and 6, respectively.
Referring to FIG. 2, the power transmission portions 5 and 6 are for frictional contact (engagement) with the corresponding sheave surfaces 62 a, 63 a, 72 a and 73 a of the pulleys 60 and 70. The first pin 3 is sandwiched between the corresponding sheave surfaces 62a, 63a, 72a, 73a, whereby power is transmitted between the first pin 3 and the pulleys 60, 70. The first pin 3 is made of a high-strength wear-resistant material such as bearing steel (SUJ2), for example, because it directly contributes to power transmission by the power transmission portions 5 and 6.

  The effective radius R (the winding radius R of the chain 1) with respect to the pin 3 in each pulley 60, 70 is defined as follows. That is, the effective radius R related to the pin 3 in the pulley 60 is defined as the distance in the pulley radial direction between the contact point T1 between the pulley 60 and the pin 3 and the central axis C1 of the pulley 60. The contact point T1 is, for example, each of the sheave surfaces 62a and 63a of the pulley 60 and one end (the upper end in FIG. 2) in the orthogonal direction V to be described later of the corresponding power transmission portions 5 and 6 of the pin 3. A contact point.

  Similarly, the effective radius R related to the pin 3 in the pulley 70 is defined as a distance in the pulley radial direction between the contact point T2 between the pulley 70 and the pin 3 and the central axis C2 of the pulley 70. The contact point T2 is, for example, each of the sheave surfaces 72a and 73a of the pulley 70 and one end (the upper end in FIG. 2) in the orthogonal direction V to be described later among the corresponding power transmission portions 5 and 6 of the pin 3. A contact point.

Referring to FIGS. 4 and 5 again, the second pin 4 (also referred to as a strip or an interpiece) is a rod-like body formed in the same material as the first pin 3 and extending in the chain width direction W. is there. Regarding the chain traveling direction X, the second pin 4 is formed thinner than the first pin 3.
The first pin 3 is loosely fitted in the front through-hole 9 of one link 2 so that it can move (rotate) relative to the link 2 and is press-fitted into the rear through-hole 10 of the corresponding other link 2. The relative rotation with respect to the link 2 is restricted by being fixed (fitted).

  Specifically, the first pin 3 is loosely fitted in the front through-hole 9 of the link 2 in the first row 51 so as to be able to rotate relative to the link 2 in the first row 51, and The relative rotation of the second row 52 with respect to the link 2 is restricted by being press-fitted and fixed in the rear through-hole 10 of the link 2 in the second row 52. Similarly, the first pin 3 is loosely fitted in the front through hole 9 of the link 2 in the second row 52 and is press-fitted and fixed in the rear through hole 10 of the link 2 in the third row 53.

Further, the second pin 4 is press-fitted and fixed (fitted) to the front through hole 9 of one link 2 to restrict relative rotation with respect to the link 2 and the rear through hole 10 of the corresponding other link 2. It is possible to move relative to the link 2 (rotate).
Specifically, the second pin 4 is press-fitted and fixed in the front through hole 9 of the link 2 in the first row 51, and relative rotation with respect to the link 2 in the first row 51 is restricted, and the second pin 4 is It is loosely fitted in the rear through-hole 10 of the link 2 in the second row 52 so that it can move (rotate) relative to the link 2 in the second row 52. Similarly, the second pin 4 is press-fitted and fixed in the front through-hole 9 of the link 2 in the second row 52 and is loosely fitted in the rear through-hole 10 in the link 2 in the third row 53.

With the above configuration, when the links 2 adjacent to each other in the chain traveling direction X bend each other, the corresponding first pins 3 are in rolling contact with the adjacent second pins 4.
In addition, the locus of the contact line T between the first pin 3 and the second pin 4 adjacent to the first pin 3 is set to be an involute curve.
Specifically, the contact part 12 which can contact the adjacent 2nd pin 4 among the surrounding surfaces 11 (outer peripheral surface) of the 1st pin 3 is formed in cross-sectional involute shape. Moreover, the contact part 14 which can contact the corresponding 1st pin 3 among the surrounding surfaces 13 (outer peripheral surface) of each 2nd pin 4 is formed in the flat surface (cross-sectional linear shape). This flat surface includes a flat surface orthogonal to the chain traveling direction X.

  With reference to FIGS. 2 and 4, the feature of the present embodiment is that the length E2 of the second pin 4 in a free state (a state where it is not engaged with any of the pulleys 60 and 70). Is shorter than the length E1 of the first pin 3 in the free state (E2 <E1), and the first pin 3 is connected to the corresponding sheave surfaces 62a, 63a, 72a, The pair of end portions 17 and 18 of the second pin 4 are in light contact with the corresponding sheave surfaces 62a, 63a, 72a and 73a in a state of being elastically contracted by being sandwiched between 73a. In the point.

  4 and 5, the length E1 of the first pin 3 refers to the distance between the pair of end portions 15 and 16 in the longitudinal direction of the first pin 3 in a free state. The distance between the pair of power transmission units 5 and 6 at one end (the upper end in FIG. 5) of the first pin 3 in the orthogonal direction V. The orthogonal direction V refers to a direction orthogonal to both the chain traveling direction X and the chain width direction W.

Similarly, the length E2 of the second pin 4 refers to the distance between the pair of end portions 17 and 18 in the longitudinal direction of the second pin 4 in the free state. The distance between the pair of end portions 17 and 18 at one end in the orthogonal direction V (upper end in FIG. 5).
The positions of the first pins 3 in the chain width direction W are aligned with each other. Similarly, the positions of the second pins 4 in the chain width direction W are aligned with each other. And the 1st pin 3 and the 2nd pin 4 have the center parts 19 and 20 of the longitudinal direction arranged in the chain advancing direction X, respectively. Thereby, in the chain straight line portion, the distance F1 between one end 15 of the first pin 3 and one end 17 of the second pin 4 and the other end 16 of the first pin 3. And the other end 18 of the second pin 4 are equal (F1 = F2).

FIG. 6 is a front view showing the first pin 3 of the chain 1 as a single unit, and the first pin 3 above the white arrow indicates the first pin 3 in a free state, The lower first pin 3 indicates the first pin 3 in a state of being sandwiched by the pulley 60.
Referring to FIG. 6, the length E1 of the first pin 3 in the free state (hereinafter also simply referred to as the length of the first pin 3) is set to 24 mm, for example. When the first pin 3 is sandwiched between the pair of sheave surfaces 62 a and 63 a of the pulley 60, the pair of end portions 15 and 16 extends from the corresponding sheave surfaces 62 a and 63 a of the pulley 60 in the chain width direction W. A pressing force H (compression load) is applied. The maximum pressing force Hmax at this time is set to about 1000 N, for example.

  When the first pin 3 receives the maximum pressing force Hmax, the first pin 3 is elastically contracted by a maximum elastic contraction amount Jmax (for example, 30 μm) in the longitudinal direction, and the length becomes E3 (E3 = E1−Jmax). ). The maximum elastic contraction amount Jmax of the first pin 3 is set to, for example, 40% of the allowable elastic contraction amount of the first pin 3. Here, the allowable elastic contraction amount refers to the maximum value of the contraction amount that the first pin 3 can elastically contract in the longitudinal direction.

The state when the first pin 3 is sandwiched between the pulleys 70 is the same as described above.
FIG. 7 is a front view showing the second pin 4 of the chain 1 as a single unit, and the second pin 4 above the white arrow indicates the second pin 4 in a free state, The lower second pin 4 indicates the second pin 4 in a state of light contact with the pulley 60.
6 and 7, the length E2 of the second pin 4 in the free state (hereinafter also simply referred to as the length of the second pin) is greater than the length E1 of the first pin 3. The difference G is shortened (E2 = E1-G).

  The difference G, that is, the difference G between the length E1 of the first pin 3 and the length E2 of the second pin 4 is 20 to 100% (0.2 Jmax) of the maximum elastic contraction amount Jmax of the first pin 3. ≦ G ≦ 1.0 Jmax). Thereby, the length E2 of the second pin 4 in the free state is set shorter by 5 to 50 μm than the length E1 of the first pin 3. That is, the difference G is set to 5 to 50 μm.

The lower limit of the difference G between the length E1 of the first pin 3 and the length E2 of the second pin 4 is 30% or more of the maximum elastic contraction amount Jmax of the first pin 3 (0.3 Jmax ≦ G ) Is more preferable. Similarly, the upper limit of the difference G is more preferably 80% or less (G ≦ 0.8 Jmax) of the maximum elastic contraction amount Jmax of the first pin 3.
When the first pin 3 receives a pressing force H from the pulley 60, the first pin 3 elastically contracts in the longitudinal direction, and one end of the pair of end portions 17 and 18 of the second pin 4 in the orthogonal direction V corresponds to the pulley 60. Lightly contact the sheave surfaces 62a, 63a (see the lower side of the white arrow in FIG. 7). At this time, the pressing force K received from the corresponding sheave surfaces 62a and 63a by the pair of end portions 17 and 18 of the second pin 4 is about 0 to 800N. This pressing force K is 0 to 80% of the maximum pressing force Hmax received by the pair of end portions 15 and 16 of the first pin 3. At this time, the pair of end portions 17 and 18 of the second pin 4 are merely in light contact with the corresponding sheave surfaces 62 a and 63 a of the pulley 60, and between the second pin 4 and the pulley 60. There is virtually no transmission of power.

The state when the second pin 4 is sandwiched between the pulleys 70 is the same as described above.
As described above, according to the present embodiment, the first pin 3 is sandwiched between the pair of sheave surfaces 62a, 63a, 72a, 73a facing each other of the pulleys 60, 70, so that the chain 1 Power can be transmitted between the pulleys 60 and 70.
Further, when the first pin 3 is engaged with the pulleys 60 and 70, the pair of end portions 17 and 18 of the second pin 4 are respectively connected to the corresponding sheave surfaces 62a, 63a, Since the second pin is moderately restrained by the corresponding sheave surfaces 62a, 63a, 72a, 73a by making light contact with 72a, 73a, the occurrence of vibration of the second pin 4 is prevented in advance. Noise during chain drive can be significantly reduced.

  Further, the pair of end portions 15 of the first pin 3 receives the pressing force K received when the pair of end portions 17, 18 of the second pin 4 lightly contacts the corresponding sheave surfaces 62 a, 63 a, 72 a, 73 a. , 16 is set to 0% or more of the maximum pressing force Hmax received, the occurrence of vibration of the second pin 4 can be reliably prevented. In addition, since the pressing force K received by the second pin 4 is 80% or less of the maximum pressing force Hmax received by the first pin 3, the second pin 4 is excessively pressed by the pulleys 60 and 70. Therefore, it is possible to prevent the torque cross from increasing.

  Furthermore, since the difference G between the length E1 of the first pin 3 in the free state and the length E2 of the second pin 4 is set to 20% or more of the maximum elastic contraction amount Jmax of the first pin 3, The second pin 4 can be prevented from being excessively pressed by the pulleys 60 and 70 to increase the torque cross. Further, since the difference G is set to 100% or less of the maximum elastic contraction amount Jmax of the first pin 3, the second pin 4 and the pulleys 60, 70 are reliably achieved with light contact. Generation of vibration of the pin 4 can be reliably prevented.

  In other words, since the difference G between the length E1 of the first pin 3 in the free state and the length E2 of the second pin 4 is 5 μm or more, the second pin 4 is connected to each pulley 60, 70. It is possible to prevent the torque loss from being excessively increased. Further, since the difference G is set to 50 μm or less, it is possible to reliably achieve the light contact between the second pin 4 and the pulleys 60 and 70 and reliably prevent the vibration of the second pin 4 from occurring. it can.

  Further, the distance F1 between one end 15 of the first pin 3 and one end 17 of the second pin 4, the other end 16 of the first pin 3 and the second pin 4. Since the distance F2 between the other end portions 18 of the second pins 4 is equal, both the pair of end portions 17 and 18 of the second pin 4 can be pressed against each other in a balanced manner. 4 can be more reliably prevented from occurring.

  Furthermore, the first pin 3 is loosely fitted into the front through hole 9 of the corresponding link 2 and is press-fitted and fixed to the rear through hole 10 of the corresponding link 2, and the second pin 4 is fixed to the corresponding link 2. The front through hole 9 is press-fitted and fixed, and is loosely fitted into the rear through hole 10 of the corresponding link 2. Thereby, when the power transmission parts 5 and 6 of the first pin 3 come into contact with the corresponding sheave surfaces 62a, 63a, 72a and 73a of the pulleys 60 and 70, the corresponding second pin 4 is The links 2 can be bent by rolling and sliding contact with the pins 3.

At this time, between the first and second pins 3 and 4 that are in contact with each other, the rolling contact component is large and the sliding contact component is extremely small. As a result, the first pin 3 is connected to the sheave surfaces 62a and 63a. , 72a, 73a hardly rotate, so that friction loss can be reduced and high transmission efficiency can be ensured.
Moreover, the locus | trajectory of the mutual contact line T of the adjacent 1st and 2nd pins 3 and 4 is made to draw an involute shape substantially, Therefore The 1st pin 3 is sequentially set to each pulley 60,70. It is possible to further suppress the occurrence of string vibration motion in the chain 1 when biting. As a result, noise during driving of the chain 1 can be further reduced.

In this way, the continuously variable transmission 100 with excellent transmission efficiency and quietness can be realized.
The present invention is not limited to the above embodiment. For example, the length E1 of the first pin 3 may be shorter or longer than the above exemplified value. Further, the maximum pressing force Hmax received by the first pin 3 may be smaller or larger than the above exemplified value. Furthermore, the ratio of the maximum elastic contraction amount Jmax to the allowable elastic contraction amount of the first pin 3 may be smaller or larger than the above-exemplified value.

Furthermore, although the length E1 of each first pin 3 is defined by the length between the pair of power transmission units 5 and 6 at one end in the orthogonal direction V, the pair of powers at the same position in the orthogonal direction V is defined. You may define as the length between the transmission parts 5 and 6. FIG.
The difference G between the length E1 of the first pin 3 and the length E2 of the second pin 4 only needs to be within a range of 20 to 100% of the maximum elastic contraction amount Jmax of the first pin 3. Depending on the value of the maximum elastic contraction amount Jmax, it may be smaller than 5 μm or larger than 50 μm.

Furthermore, the cross-sectional shape of the contact portion 12 of the first pin 3 may not be an involute curve. Further, the cross-sectional shape of the contact portion 14 of the second pin 4 may not be a linear shape. Further, the first and second pins 3 and 4 may not be press-fitted and fixed to the corresponding link 2. Further, the arrangement of the front through hole 9 and the rear through hole 10 of the link 2 may be interchanged.
Further, the front through hole 9 and the rear through hole 10 of each link 2 may be communicated with each other as long as their functions are not impaired. Specifically, a communication groove that allows the through holes 9 and 10 to communicate with each other may be formed in a column portion disposed between the front through hole 9 and the rear through hole 10 of each link 2. Thereby, the stress concentration of the peripheral part of each said through-hole 9 and 10 can be relieve | moderated more. The present invention includes such a shape of the through hole.

Furthermore, a member having a power transmission unit similar to the power transmission units 5 and 6 is disposed on each of the pair of end portions 17 and 18 of the first pin 3, and the first pin 3 and the power transmission unit are connected to each other. It is good also as providing the power transmission block containing the member which has, and making this a 1st power transmission member.
Further, the present invention is not limited to a mode in which the groove widths of both the drive pulley 60 and the driven pulley 70 are changed, and only one of the groove widths may be changed and the other may be a fixed width that does not change. good. Furthermore, although the aspect in which the groove width continuously changes (steplessly) has been described above, the groove width may be changed stepwise or may be applied to other power transmission devices such as a fixed type (stepless). .

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view schematically showing a main configuration of a chain type continuously variable transmission as a power transmission device including a power transmission chain according to an embodiment of the present invention. It is a partial expanded sectional view of the drive pulley (driven pulley) and chain of FIG. It is a perspective view which shows typically the structure of the principal part of a chain. It is a cross-sectional top view of the principal part of the chain shown in FIG. It is sectional drawing which follows the II-II line | wire of FIG. 4, and has shown the chain linear part. It is a front view which shows the 1st pin of a chain by itself, the 1st pin of the upper part of a white arrow shows the 1st pin in a free state, and the 1st pin of the lower side is The 1st pin in the state clamped by the pulley is shown. It is a front view which shows the 2nd pin of a chain by itself, the 2nd pin of the upper part of a white arrow shows the 2nd pin in a free state, and the 2nd lower pin is The 2nd pin in the state which lightly contacted the pulley is shown.

Explanation of symbols

1 Chain (Power transmission chain)
2 link 3 first pin (first power transmission member)
4 Second pin (second power transmission member)
17 ends (one of a pair of ends of the second power transmission member)
18 ends (the other of the pair of ends of the second power transmission member)
60 Drive pulley (first pulley)
62a, 63a Sheave surface 70 Driven pulley (second pulley)
72a, 73a Sheave surface 100 continuously variable transmission (power transmission device)
E1 Length (first power transmission member) E2 Length (second power transmission member) G Difference Hmax (Maximum pressing force Jmax received from the corresponding sheave surface of the first power transmission member) Jmax Maximum Elastic shrinkage K (pressing force received by the end of the second power transmission member from the corresponding sheave surface)

Claims (5)

A plurality of links, and a first and a second power transmission member that connect the links to each other and are in rolling contact with each other, and the first power transmission member is disposed between a pair of sheave surfaces facing each other of the pulley. In the power transmission chain that is sandwiched and transmits power between the first power transmission member and the pulley,
The second power transmission member is shorter than the first power transmission member in a free state,
The first power transmission member is sandwiched between the pair of sheave surfaces and is elastically contracted so that the pair of end portions of the second power transmission member are in light contact with the corresponding sheave surfaces. A characteristic power transmission chain.   The pressing force received from the corresponding sheave surface by the end portion of the second power transmission member when the end portion of the second power transmission member makes light contact with the corresponding sheave surface according to claim 1 A power transmission chain characterized in that the end of the power transmission member is 0% to 80% of the maximum pressing force received from the corresponding sheave surface.   3. The difference between the length of the first power transmission member in the free state and the length of the second power transmission member according to claim 1 or 2 is 20 to 100% of the maximum elastic contraction amount of the first power transmission member. A power transmission chain characterized by being.   4. The power transmission chain according to claim 1, wherein a difference between the length of the first power transmission member in the free state and the length of the second power transmission member is 5 to 50 [mu] m. A first pulley and a second pulley each having a pair of conical sheave surfaces facing each other, and wound around these pulleys and engaged with the sheave surfaces to transmit power. A power transmission device comprising the power transmission chain according to claim 4.

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