JP2002174302A - Endless belt for transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To form an end face shape of a split pin so that a pin width variation by rotation of the pin is minimized, reduce a polygonal effect and sliding of the pin to a sheave, and reduce noise and power loss. SOLUTION: In this endless belt connecting link plates by a pair of the split pins and holding two blocks between the pins, end faces of the pins are formed in round shapes in a belt longitudinal direction (an X direction). A deviation amount aA of a radial center of the round shape to a pin rotational center is determined by distributing the pin width variation μ so that the variation is equal on a positive rotation side and a negative rotation side of a rotation angle θ in regard to a rotation angle variation ηa within an application range.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission endless belt used for a belt type continuously variable transmission (CVT), and more particularly, to an end face shape of a pin in a transmission endless belt in which link plates are connected by pins. .

[0002]

2. Description of the Related Art An endless belt for transmission of this type is known as Van Doorne's Transmission in the Netherlands.
IE (VDT) (VDT; for example, Japanese Patent No. 1105154) is being put into practice. The VDT belt is formed by continuously inserting a metallic V-shaped block into a laminated steel band, and the side surface of the V-shaped block contacts the sheave surfaces of the primary and secondary pulleys in a lubricating environment. Power is transmitted by pushing the shaped blocks together.

[0003] The VDT belt can be reduced in bite pitch and polygon change amount by making the V-shaped block thinner, and is excellent in quietness.
The laminated steel belt is made of an expensive material, requires high-precision manufacturing, and generates slip loss between the laminated steel belts in a power transmission state.

Conventionally, in order to solve the above problems, for example, an endless transmission belt disclosed in Japanese Patent Application Laid-Open No. Hei 7-91498 has been proposed. The metallic belt is, as shown in FIG.
A large number of first and second blocks 2, 3 arranged in a certain order in the longitudinal direction of the belt 1, a large number of link plates 5 connecting these blocks, and a division connecting these link plates. 2 pins (rocker pins) 6
a and 6b, and spring means 7 which engages with the pins 6 and expands and contracts in the longitudinal direction of the link plate. The link plate 5 is inserted into the through holes 9, 10, 9 respectively.
The link chains 11 alternately connected by pins 6 penetrate and are connected endlessly.

The first and second blocks 2,
3 are protrusions 2a, 3 so that the back surfaces thereof abut each other.
a is formed, and pin-engaging grooves 2b and 3b are formed on opposite sides thereof, and the split pins 6a and 6b are engaged with these adjacent grooves, respectively. Further, both outer surfaces of the blocks 2 and 3 are inclined surfaces 2c and 3c so as to align with the sheave side surfaces of the respective pulley devices, and both outer end surfaces of the pins 6 also align with the sheave side surfaces. And the pin end face 6
c has an R shape on a surface orthogonal to the longitudinal direction of the belt, and can contact the sheave side surface on the pitch circle.

In the transmission endless belt 1, the torque of the pulley device is transmitted from the sheave side by contacting the first and second blocks 2, 3 and the pins 6, and further includes the link plates 5 via the pins 6. Acting as a pulling force on the link chain 11, torque is transmitted.

[0007]

The metal endless belt 1 has a first block 2, a front split pin 6b, a rear split pin 6a and a second block 3 on a substantially straight sheave side surface. In order, and then come off the sheave side in this order. In order to reduce the noise generated when the metal endless belt 1 bites into the pulley, the pitch between the pulleys (contact start position interval in the circumferential direction) is reduced as much as possible, and the polygon change amount (multiple Therefore, it is preferable that the first block 2, the front split pin 6b, the rear split pin 6a, and the second block 3 be accurately engaged in this order.

The metallic endless belt 1 is substantially linear (from a large circular arc) such that both side surfaces 2c and 3c of the first and second blocks 2 and 3 extend substantially vertically along the sheave side surface. (Including those substantially in contact with the sheave side surface due to elastic deformation or the like).
When being bent from the straight state by being engaged with the pulley, both side surfaces of each block can start contacting the sheave side surface at any position in the vertical direction. The contact start position in the circumferential direction (longitudinal direction of the belt) changes depending on the position.

For this reason, the blocks 2 and 3 may be inclined with respect to the X-axis, Y-axis and Z-axis when the pulley is engaged due to the accuracy and deformation of the sheave side surface and the block (as shown in FIG. X axis, left and right directions are Z axis, vertical directions are Y
Axis), and the sheaves may bend, causing the sheaves to start contacting the sheaves at the top or bottom of the block. In this case, the blocks 2, 3 in the circumferential direction (longitudinal direction of the belt) may contact the sheaves. The contact start position overlaps the pin 6, and the biting pitch increases by that amount, and the noise amount increases.

[0010] The Applicant has in the first and second blocks:
At positions substantially corresponding to the outer end surfaces of the split pins on the left and right outer surfaces, a projecting outer surface having a shape capable of protruding in the left-right direction and contacting the sheave side surface is formed,
An endless belt for transmission is proposed in which a total of four locations of a pair of split pins and the projecting outer surfaces of the first and second blocks contact the sheave side surface one after another at one pitch of the link chain. (Japanese Patent Application No. 11-3758
No. 05; unpublished at the time of filing this application).

According to the above proposal, the change in the contact start position with the sheave due to the inclination of the block is improved.
If the end surface shape of each of a and 6b is a flat surface shape along the sheave side surface, or is an R shape on a surface (radial direction) orthogonal to the belt longitudinal direction as in the above-described conventional technology (the above-described technique). The R shape in the direction is a shape along the side of the sheave on the pitch circle, and is substantially the same as the flat surface and the rotation of the pin at the time of biting). When the pin rotates in accordance with the effective diameter of the pulley, the actual width of the pin (relative gap between the pin and the sheave) greatly changes due to the spin (rotation) of the pin, and the contact position between the pin and the sheave (circumference) Direction and radial direction) (change in the position at which the pin starts to bite), and the above-described polygonal effect becomes apparent, causing noise. At the same time, the sliding of the pin with respect to the sheave, particularly the sliding in the radial direction increases. I will.

Further, when the pin comes into contact with the sheave at a position away from the center of rotation of the pin, the spin (rotation) of the pin causes an increase in spin loss, and the relative clearance between the pin and the sheave is reduced. Power loss occurs due to the change, particularly in the radial direction, and the power transmission efficiency is reduced.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an endless transmission belt in which the shape of the end face of the pin is improved to solve the above-mentioned problems.

[0014]

The present invention according to claim 1 (see, for example, FIGS. 2 to 8 and FIGS. 9 and 10) comprises a plurality of pins (26) having a rolling surface (31a); In a transmission endless belt (21) comprising a plurality of link plates (25) which are alternately connected to form a link chain (32), the pins have left and right outer end faces (26c). Pulley sheave side (V)
It consists of a shape and a length that can come into contact with, and the end face shape of the pin is such that the longitudinal direction of the endless belt is the X direction,
It has a curved shape (R, Rp) at least in the X direction.
An endless belt for transmission characterized by the above-mentioned.

According to a second aspect of the present invention (see, for example, FIGS. 8 and 10), the end face shape of the pin is a substantially cylindrical shape having a curved shape (R, Rp) in the X direction. 1
Endless belt for transmission described in the above.

According to a third aspect of the present invention, the pin (2
6) is a 1 having a rolling surface (31a) that can abut each other.
The endless belt for transmission according to claim 1 or 2, comprising a pair of split pins (26a, 26b).

According to a fourth aspect of the present invention, in the transmission according to any one of the first to third aspects, the curved shape is a round shape having a radius (Rp) in a range of 5 to 15 [mm]. It is on the endless belt.

The present invention according to claim 5 (for example, see FIGS. 17 to 29, particularly FIG.
a, 26b) is obtained by calculating the pin width change (ε) obtained from the gap (δ) between the pin end face (26c) and the sheave in the X direction by the rotation angle change in the pin usage range. (Ηa) the radius (Rp) center of the radius shape with respect to the pin rotation center (0) in the X direction, which is obtained by distributing the rotation angle (θ) to be equal to the positive rotation side and the negative rotation side of the rotation angle (θ). The transmission endless belt according to claim 4, wherein the transmission endless belt has a displacement amount (a, aA).

The present invention according to claim 6 is characterized in that the deviation amount (a
A) is in the range of -0.2 to +0.2 [mm],
An endless transmission belt according to claim 5.

The present invention according to claim 7 is characterized in that the deviation amount (a
The transmission endless belt according to claim 6, wherein A) is a value not including 0.

The present invention according to claim 8 (see, for example, FIG. 3, FIG. 28, and FIG. 29) provides the pair of split pins (26a, 2a).
6b) a sheet hole (30a) formed in the link plate (25) on the side opposite to the rolling surface (31a).
Is attached to the link plate, and the split pin (26b) on the front side of the pair of split pins in the direction of movement of the endless belt is rotated in the direction of movement of the endless belt (21) in the forward direction. The endless belt for transmission according to any one of claims 5 to 7, wherein the endless belt for transmission is attached to the link plate (25) at a predetermined value (f; for example, 5 °) in the forward rotation direction with respect to the Y direction orthogonal to the direction. It is in.

According to a ninth aspect of the present invention (see, for example, FIG. 28), the front split pin (26b) has a radius (Rp) center of the radius shape with respect to a rotation center (0) of the pin. The transmission endless belt according to claim 8, wherein the endless belt (21) has a predetermined displacement (aA) on the rear side in the moving direction of the endless belt (21).

According to a tenth aspect of the present invention, the radius of the round shape is approximately 10 [mm], and the predetermined deviation amount (ah) is approximately 0.03 [mm]. 9. The transmission endless belt according to item 9.

The present invention according to claim 11 (for example, see FIG. 2 to FIG. 8) is that the pins (2
6) having at least one block (22) (23) having a through-hole (35) penetrating through the link chain (32) in the X-direction in the X direction. The pins (26a, 26) on the outer side surface
At a position substantially corresponding to the outer end face (26c) of (b), a projecting outer face (45) projecting in the left-right direction and having a shape capable of contacting the sheave side face (V) of the pulley is provided. Item 10 is the endless transmission belt according to any one of Items 3 to 9.

According to a twelfth aspect of the present invention (see, for example, FIGS. 2 to 8), the block includes a projection (41) that can contact each other in the X direction and the split pin (2) on the opposite side.
6a, 26b) having first and second blocks (22, 23) having concave grooves (40) for receiving the pair of split pins (26) at one pitch of the link chain.
a, 26b) and the projecting outer surfaces (45) of the first and second blocks (22, 23).
12. The endless belt for transmission according to claim 11, wherein a total of four places are arranged so as to sequentially contact the sheave side faces.

Note that the reference numerals in parentheses are for comparison with the drawings, but this is for the sake of convenience to facilitate understanding and speeding up of the present invention in correspondence with the embodiment. This does not have any effect on the configuration described in the claims.

[0027]

According to the first aspect of the present invention, since the end face of the pin has at least a curved shape in the X direction, the end face has a flat surface or a curved shape in the Y direction. The amount of change in the pin width due to the rotation of the pin when the pin bites into the pulley can be reduced, which reduces the polygonal effect, reduces the deformation of the pin and sheave in the width direction, and improves the durability. Slip with,
In particular, slippage in the radial direction and the rotation (spin loss) direction can be reduced, power loss can be reduced, and power transmission efficiency can be improved.

According to the second aspect of the present invention, since the curved shape is substantially cylindrical, the pin end face can be manufactured by two-dimensional grinding or the like, and the pin end face is formed into a spherical shape. The manufacturing accuracy can be improved and the processing accuracy can be improved as compared with the one in which the shape is changed. Further, the influence of the change in the curved shape in the X direction on the actual width of the pin is significantly larger than that due to the change in the Y direction. And the cylindrical shape that changes only in the X direction does not significantly affect the noise and power performance of the belt due to practical use. In addition, by forming the belt end surface into a cylindrical shape, the Hertz stress is reduced as compared with a spherical shape, and the endless belt is pressed against the sheave side surface of the pulley to secure a predetermined torque capacity. Strength can be maintained.

According to the third aspect of the present invention, the pin is
Because the split pins have rolling surfaces that can abut each other,
It is possible to obtain a highly reliable structure with sufficient strength and reliable rolling by reducing power loss.

According to the fourth aspect of the present invention, the curved shape is a round shape having a radius in the range of 5 to 15 [mm]. The width variation can be kept within an acceptable range for belt performance.

According to the fifth aspect of the present invention, the amount of deviation of the radius center of the round shape from the center of rotation of the pin with respect to the center of rotation in the X direction is determined by the amount of change in the pin width and the amount of change in the pin width. It is set by equalizing on the side and the negative rotation side (not necessarily separated into a positive value and a negative value, but may be both positive and negative values on both rotation sides) In addition, the pin end surface shape can be set so that the pin width variation is minimized, and a high-performance endless belt with reduced noise and power loss can be obtained.

According to the sixth aspect of the present invention, when the deviation amount is in the range of -0.2 to +0.2 [mm], the pin width change amount is large at the mounting angle of the link pin of the divided pin. It is possible to provide an endless belt that can be placed in a range where there is no influence and has performance that does not substantially hinder use.

According to the seventh aspect of the present invention, when the deviation of the radius center (X coordinate) of the radius of the pin end face from the pin rotation center is 0, the pin width change within the pin rotation angle change range is: With the split pin on the front side in the belt moving direction, the maximum is at the pin rotation angle (same as the pin link plate mounting angle) at the position where the belt starts to bite into the pulley, and at the pin rotation angle at which the belt rotates and the pin rotation ends. As a result, the pin width change amount becomes large within the pin rotation angle change range. However, when the deviation amount does not include 0, that is, when the pin rotation center and the radius center (X coordinate) of the round shape of the pin end face are different from each other. (The shift direction is the positive side (rightward direction) with respect to the Y-axis toward the center of the pulley radius, depending on the pin link plate mounting angle.
Alternatively, the pin width change amount can be suppressed to a small value within the pin rotation angle change range.

According to the eighth aspect of the present invention, since the split pin on the front side in the belt moving direction is attached to the link plate at a predetermined value in the forward rotation direction, the endless belt is engaged with the pulley when the endless belt is engaged with the pulley. The split pin is rotated in the negative rotation direction from the predetermined value in the positive rotation direction when the belt is substantially in the direct state, and has a predetermined value in the negative rotation direction when the pulley is completely engaged, and is divided. The rolling surface of the pin can be used on both sides with the center line interposed therebetween, which can be advantageous in terms of strength and, together with the setting of the above-mentioned predetermined shift amount, can reduce the pin width change amount.

According to the ninth aspect of the present invention, the predetermined shift amount of the front divided pin is shifted to the rear side (positive side) in the belt moving direction. Accordingly, the amount of change in the pin width can be reduced.

According to the tenth aspect of the present invention, when the radius of the radius of the pin end surface is approximately 10 [mm] and the predetermined deviation amount is approximately 0.03 [mm], the effective pulley diameter is the minimum diameter. When applied to a practical endless belt having a maximum diameter of about 28 [mm] and a maximum diameter of about 69 [mm], the pin width variation can be minimized to provide an optimum pin end shape.

According to the eleventh aspect of the present invention, the projecting outer side surface is formed on the block so that the contact area with the side surface of the sheave is increased.
Since it is limited to a predetermined range near the pitch line so as to correspond to the pin, the block and the pin can surely come into contact with the sheave side surface in combination with the shape of the pin end surface described above.

According to the twelfth aspect of the present invention, a total of four locations including the outer end faces of the pair of split pins and the projecting outer faces of the first and second blocks are provided for one pitch of the link chain. The row ensures contact with the side of the sheave, which reduces the bite pitch and reduces the polygonal effect. This is a tension-type endless belt that can be manufactured with high transmission efficiency and relatively low cost. However, it is possible to provide an endless belt having excellent performance with reduced noise and improved durability.

[0039]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 2 is a side view showing a metal endless belt for transmission according to the present invention, FIG. 3 is an enlarged side view showing a portion where the endless belt is engaged with a pulley, FIG. 4 is a front sectional view, and FIG. 5 is a plan view. . Similarly to the belt 1, the transmission endless belt 21 includes a number of first and second blocks 22 and 23 arranged in a certain order in the longitudinal direction, and a number of link plates 25 and Pin 26
And a spring means 27 which engages with these pins to extend and contract in the longitudinal direction of the link plate 25.

The link plate 25 is shown in FIGS.
As shown in detail in (c), a pin hole formed of a predetermined shape of a steel plate manufactured by fine blanking or the like, and formed at both ends with holes 30a and 30b for receiving a pair of divided pins 26a and 26b, respectively. 30 are formed respectively. The pin 26 is composed of a pair of mirror-symmetrical split pins (rocker pins, sheet pins) 26a and 26b whose opposing surfaces are rolling surfaces 31a, and a side surface 31b opposite to the rolling surface is outside the link plate 25. It comes into contact with the sheet hole 30a and is fitted so as to be integrated with the link plate. Then, the link plates 25 are alternately connected by the pins 26 to form the link chains 3.
Constituting No. 2.

2, 4, 5 and 6 (d) and 6 (e), the center of the rank G, which is a row in the horizontal direction of the link chain 32.
A spring link 27 having a shape is provided between the two pins 26 so as to extend and contract. The spring means 27 is provided at every other rank G
, And the contraction force is applied to each pin 26 to apply a frictional force between the block and the link plate with which each pin is in contact, particularly the belt assembly state and the belt slack state. In this case, the frictional force prevents the pins from being displaced in the axial direction and falling off.

Further, as shown in FIGS. 3 and 5, with one split pin 26a is seated against rotation in the seat hole 30a of the link plate 25 a predetermined rank G ₁ in the lateral one row of said link chain, other the other split pin 26b into the hole 30b are loosely fitted, and the other divided pin 26b to the sheet hole 30a of the link plate 25 No. G ₂ adjacent to the rank G ₁ is seated non-rotatably, these two pins The ranks G ₁ and G ₂ can be bent by the rolling surfaces 31a of the rolling members 26a and 26b being in contact with each other, whereby the endless belt 21 corresponds to the effective pulley diameter set by a pair of sheave intervals. The power can be transmitted by continuously changing the speed by the speed change operation (change of the effective diameter) of the pulley.

On the other hand, as shown in FIGS. 4 and 5, the pins 26 extend to the left and right of the ranks G.
The first and second blocks 22 and 23 are in contact with each other. The first and second blocks 22 and 23 are mirror-symmetrical. Hereinafter, the first block 22 will be described, but the same applies to the second block 23. Block 2
2 and 23, as shown in FIGS. 4 and 6, have a substantially rectangular through hole 35 at the center and an upper side 3 around the through hole 35.
6, a lower side portion 37 and left and right side portions 39, 39. The link chain 32 is disposed in the through hole 35 so as to penetrate therethrough.
At the pin 26.

As shown in detail in FIG. 7, the block 22 (23) has a groove 40 on one surface in the front-rear direction on the left and right sides 39, and a protrusion 41 on the opposite surface.
Are formed, and the thickness thereof is substantially the same in the radial direction. In the concave groove 40, the dividing pin 2
One of the pins 6a and 26b is received and abuts near the center in the radial direction on the opposite side surface 31b of the pin, and its upper and lower surfaces are formed in an arc shape such that there is a gap allowing relative rotation between the block and the pin. It is configured.
Further, projections 42a and 42b are formed on the upper and lower surfaces of the concave groove 40 so as to hold the pins 26a and 26b in the front-rear direction (the longitudinal direction of the belt). The projecting amount j of the block 22 (23) is configured to be small as long as the minimum winding angle on the pulley can be maintained.

As shown in detail in FIG. 7 (b), the outer surface 45 of the concave groove 40 in the block 22 (23) is formed so as to project a predetermined amount in the left-right direction (axial direction of the pin). I have. The projecting outer surface 45 has an inclination angle β substantially the same as the sheave side surface V, and
In this case, only the protruding outer surface 45 can come into contact with the sheave side surface. The projecting outer surface 45 is provided with the split pins 26a, 26
b, in a position substantially corresponding to the outer end surface 26c, and in a vertical direction (radial direction), in a vertical direction (radial direction), a substantially linear shape having a predetermined inclination angle β (consisting of a large arc, elastic deformation, etc.) so as to match the sheave side surface V. In addition, the belt has a substantially straight shape in the front-rear direction (longitudinal direction of the belt), and therefore has a substantially flat shape with a predetermined area. The protruding outer surface 45 is located at a position substantially corresponding to the pin 26 in the longitudinal direction of the belt, specifically, near the pitch line PP of the belt, and slightly shorter than the radial length L of the concave groove 40. Consists of length l. Surfaces 46a and 46b are also formed above and below the concave groove in the through hole 35 of the block outer portion 39, and these surfaces 46a and 46b define the width of the link chain 32 as shown in FIG. At the same time, the blocks 22 and 23 are brought into contact with the outermost link plate 25 to make the blocks 22 and 23 swing smoothly with respect to the link plate 25.

On the other hand, as shown in FIG.
(While only one of the divided pins 26a is described, the same applies to the other divided pin 26b because of the mirror symmetry, the dimension is substantially the same as the protruding outer surface 45 of the block in the left-right (width) direction. The pin width on the pitch line is denoted by B), and both outer end surfaces 26c, 26c have the same inclination angle β as the sheave side surface similarly to the protruding outer surface 45,
The two outer end surfaces 26c of the pin, together with the two projecting outer surfaces 45 of the block, contact the sheave side surfaces. Pin outer end surface 26
c is arranged so as to substantially correspond to the projecting outer surface 45 of the block in the belt longitudinal direction, and its radial length m is substantially the same as the length 1 of the block projecting outer surface 45. Or slightly larger than the length l.

The split pins 26a (26b) are
As shown in detail in (a), a rolling surface 31a formed of a curved surface having a large curvature and a seat surface 31b formed on the opposite side and formed of a curved surface formed by a combination of arcs seated in a link plate seat hole 30a. And its outer end surface 26
As shown in FIG. 8B, c is a straight line having the predetermined inclination angle except for upper and lower round portions when viewed from the front (when viewed from the longitudinal direction of the belt). And the pin outer end surface 2
6c is a curved surface R such as an arc having a predetermined radius in a plan view (as viewed from the radial outside) as shown in FIG. The top portion s of the curved surface R is located at a position deviated by a predetermined amount toward the rolling surface 31a with respect to the center line (X-axis) in the front-rear direction of the pin, so that the pin outer end surface 26c is deflected toward the rolling surface. It is designed to contact the sheave side surface over a radial length m at the top portion s of the surface R. In addition, from the front view of the end surface 26c of the pin 26 (Y direction) [(b)
Reference] is linear, but like a conventional pin, it may be in a front view as well as in a curved shape. In the pitch line PP, the length B in the left-right direction (width direction) is set so as to be substantially the same as the pins 26a (26b) and the blocks 22 (23). In the pitch (ie, the length of one link plate), 2
Divided pins 26a, 26b and two blocks 22,
A total of four of the 23 projecting outer surfaces 45, 45 are divided at substantially equal intervals, and can contact the sheave side surface. The curved shape of the pin end surface is desirably an arc surface (R shape) having a predetermined center. However, the shape is not limited to a true circular shape, but may be an ellipse or any other curved shape such as a curved surface.

Further, the shape of the outer end face 26c of each of the split pins 26a and 26b (hereinafter simply referred to as the pin 26) will be described in detail with reference to FIGS. Endless belt 21
The width B (the length in the pin axial direction; see FIG. 4) of the pin 26 at which the left and right outer end surfaces 26c of the pin are brought into contact with the sheave by engaging with the pulley is the minimum value of the gap (skin) between the pin end surface and the sheave. When the pin is rotated, the clearance between the pin end face and the sheave changes, and the actual pin width changes. That is, when the belt 21 bites into the pulley, the belt in a straight line state is bent (bent) along the effective diameter of the pulley, but at this time, the pin 26 is rotated, and the gap between the pin end surface and the sheave is generated. Contact position of pin end face based on actual pin width
Is determined.

As shown in FIG. 9, the center of rotation 0 of the split pins 26a and 26b rotating on the rolling surface 31a with respect to each other is defined by a line (Y axis) toward the center of the pulley of the pin 26 and the Y axis.
At an intersection with a line (circumferential direction) (X-axis) along the belt longitudinal direction at 1/2 of the radial length m of the pin on the shaft,
When the pin is rotated by an angle θ ° about the center of rotation 0, an arbitrary A
The general formula for calculating the value of the gap (skin) δ (both sides) between the point and the sheave is as follows.

[0050]

(Equation 1) Where δ: clearance with sheave [mm] R ₀ : radial position of pin rotation center [mm] A ₀ : (x ₀ , y ₀ ): x, y coordinates [mm] of A ₀ point A ₁ : (x ₁ , y ₁ ): x, y coordinates of point A ₁ [mm] θ: pin rotation angle [°] (positive left rotation) α: angle of point A ₀ [°] r: pin rotation center to point A ₀ distance [mm] beta: sheave side angle [°] c: fix pin end face shape ^{[mm] ± * 1: (} +) when x ₀ is positive, (-) ± when x ₀ is negative ^* 2: (+) when y ₀ is positive, (-) ± when y ₀ is negative ^* 3: (+) when x ₀ is negative, (-) when x ₀ is positive

Here, regarding the correction value c of the pin end surface shape, if the pin end surface 26c is a flat (flat) surface, c = 0, and if the pin end surface shape is a circular arc, the correction value c Analysis of c is as follows.

First, in the case where the pin end surface 26c has a round (R) shape on the X axis, that is, in the case of a cylindrical shape having the same dimensions in the pulley radial direction (pin vertical direction in FIG. 9; on the Y axis), FIG. As shown by reference, the correction value c of the pin end surface shape is as follows.

[0053]

(Equation 2)

On the other hand, when the shape of the pin end surface is round on the Y axis, that is, when the longitudinal direction of the belt (the front-rear direction of the pin end surface in FIG. 9; on the X axis) is the same as the cylindrical shape, FIG. Is shown below with reference to FIG.

[0055]

(Equation 3)

Further, when the pin end face is inclined at the X and Y coordinates of the R shape, the correction value c of the pin end face shape is as shown below with reference to FIG.

[0057]

(Equation 4)

Next, the gap δ at each point of the X coordinate or the Y coordinate based on the above equation is specifically shown in FIGS. 13 to 24 using the pin rotation angle θ as a parameter.

FIGS. 13 to 16 show the relationship between the pin having a flat end surface (c = 0) and the gap δ (both sides). Specifically, FIGS. 13 and 14 show x ₀ = 0. In other words, the gap δ at each point of the Y coordinate on the Y line toward the center of the pulley is shown, and FIG. 13 shows that the effective diameter of the pulley (the radial position R ₀ of the pin rotation center ₀ ) is a small diameter, for example, the minimum diameter position in design. FIG. 14 shows a case where the effective diameter of the pulley is a large diameter, for example, the maximum diameter in design.

FIGS. 15 and 16 show the gap δ at each point of the X coordinate at the center of the pin in the radial direction (on the X axis), ie, y ₀ = 0, and FIG. 15 shows the effective diameter of the pulley (pin rotation center). 16 shows a case where the radial position R ₀ ) is at a small diameter, for example, at a design minimum diameter position, and FIG. 16 shows a case where the pulley effective diameter is at a large diameter, for example, at the design maximum diameter.

13 to 16, the gap δ at the X coordinate is 0.02 to 0.06 [mm] while the gap δ at the Y coordinate is 0.001 to 0.005 [mm]. 13, the gap δ at each point on the Y coordinate shown in FIGS. 13 and 14 is larger than the gap δ at each point on the X coordinate shown in FIGS. This is the same tendency when the effective pulley diameter is large or small.

That is, the sensitivity of the coordinates with respect to the change of the substantial pin width B (the gap δ between the pin and the sheave) is about 10 times or more that the X coordinate is larger than the Y coordinate. The change in the pin width is as small as a few microns, and the change in the X coordinate is within a range in which even if it is neglected, there is no practically significant effect.

Therefore, the radius (R) shape of the end surface 26c of the pin 26 is set only to the X coordinate, that is, so that each point on the Y axis has the same radius (arc shape only in the direction along the X axis). Even in the case of the formed cylindrical shape, practically no significant influence occurs on a substantial change in the pin width due to the rotation of the pin.

Further, by forming the pin end surface into a cylindrical shape, it is sufficient to perform processing in only one direction (two-dimensional processing) when forming precisely with a grinding machine, so that a spherical shape requiring three-dimensional processing is required. In comparison with the above, processing becomes easy, a pin shape with high precision and high precision is obtained, and the Hertz stress is reduced to about half as compared with a spherical shape, which is preferable in terms of strength and durability. That is, in order for the belt-type continuously variable transmission to have a predetermined torque capacity, the pulley needs to hold the belt with a predetermined pressing force, and therefore, a large pressing force acts on the pin end surface from the sheave side surface. By forming the pin end face into a cylindrical shape, the Hertzian stress corresponding to the pressing force is significantly reduced as compared with the spherical shape, and the strength of the pin corresponding to the predetermined torque capacity can be secured.

It is also possible to make the pin end surface spherical in consideration of the pin width change due to the Y coordinate. In this case, as described above, the pin width change at the Y coordinate is changed to the X coordinate change. On the other hand, it is troublesome to process the spherical surface with high precision, and the Hertz reaction force is high.However, it is possible to obtain a pin end surface shape with less change in the pin width due to the rotation of the pin, overcoming the above drawbacks. Then, the pin end face shape may be spherical.

Next, the shape of the pin end face is changed to an arc (R;
The results of the specific example of the R) shape will be described with reference to FIGS. In these drawings, the pin end surface has a radius (R) shape having a predetermined radius (for example, an R radius of 10 [m
m]) is used in the form of a cylinder formed along the X axis, and the change in the gap δ at each point on the X axis is shown using the pin rotation angle θ as a parameter.

FIGS. 17 to 21 show the pulley effective diameter R _0.
17 shows the case where the deviation a of the R center with respect to the pin rotation center 0 is 0 (a = 0), that is, the R radius of the pin end face on the normal plane passing through the pin rotation center 0 in the X coordinate. When the center is located, y ₀ = 0, that is, a value on the center line (X-axis) in the radius (vertical) direction of the pin. FIG.
Is a value when the shift amount a is 0 (a = 0) and y ₀ = 1.5, that is, 1.5 [mm] in FIG. 9, which is above the center line (X-ray) (in the radial direction of the pulley). Is shown. FIG. 19 also shows that the displacement a is 0 (a = 0), y ₀ = −1.5, that is, 1.5 mm in FIG. 9, and the center line (below the X-ray (in the direction of the inner diameter of the pulley)). ).

FIG. 20 shows that y ₀ = 0 (on the center line) when the center of the R radius of the pin end face is shifted to the right (positive direction) by 0.1 mm in the X coordinate (a = 0.1). (On the X-axis). FIG. 21 shows that a = −0.1, that is, at the X coordinate, 0.1 in the left direction (negative direction) with respect to the pin rotation center.
It shows the value of y ₀ = 0 (on the center line) when there is a deviation [mm].

FIGS. 22 to 24 show the pulley effective diameter R _0.
Shows the case of the maximum diameter, and FIG. 22 shows that the displacement amount a is 0 (a =
0) indicates a value of y ₀ = 0 (center line; on the X axis). FIG.
3 indicates that the deviation amount is 0.1, that is, in the X coordinate, the center of the R shape of the pin end face is rightward (positive direction) with respect to the pin rotation center.
FIG. 24 shows the value of y ₀ = 0 when the displacement is 0.1 mm, and FIG. 24 shows that the deviation amount is a = −0.1, that is, in the X coordinate, the center of the R shape of the pin end face is the pin rotation. Y ₀ when shifted by 0.1 [mm] to the left (negative direction) from the center
= 0.

FIG. 17, FIG. 18, FIG. 19, and FIG.
5. As is apparent from comparison with FIG.
Is a flat surface, and at each pin rotation angle θ, there is a direct proportionality so that the gap δ increases as the X coordinate increases in the (+) and (−) directions.
When the shape is formed, the gap δ becomes as small as several microns, and the change of the gap δ at each X coordinate has a minimum value. This is true even at the center position of the Y axis (y ₀ = 0; on the X axis) (FIG. 1).
7), the same tendency exists even at a position deviated upward or downward from the center position (X axis) (see FIGS. 18 and 19), and even when the effective diameter of the pulley is small (see FIG. 17), the diameter becomes large. However, the same tendency exists (see FIG. 22).

In contrast to y ₀ = 0 (center line) shown in FIG. 17, y ₀ = 1.5 (1.5 [m
m], about +3 microns, y ₀ = −1.
5 (1.5 mm below the pin)
The effective pin width by 3 microns, X coordinate, increases or decreases, but this is reduced by the deflection of the pin in the Y direction.

Therefore, the pin end face 26c is formed in an arc shape at least in the X coordinate, as compared with a plane end face (a conventional technique having a round shape in the Y-axis direction). However, the change amount of the clearance δ (substantial pin width) with respect to the pin rotation angle is small, which is preferable.

The influence of the center of the R shape of the pin end face is
20 to 24, when the center of the R shape is moved with respect to the pin rotation center 0 on the X coordinate, the minimum value of the clearance between the pin end face and the sheave and the X coordinate value thereof change. The same tendency exists even when the effective diameter of the pulley around which the belt is wound changes (see FIGS. 20 and 23).

Next, the amount of change in the pin rotation angle will be described with reference to FIGS. 25 and 26. Each link 25 is bent by the belt being engaged with the pulley, and the pin 26 is held integrally with the link.
Is the same as the bending angle η of the link.

The radius of the pin rotation center (≒ pitch circle) from the center of the pulley (effective pulley diameter) is R ₀ , and the link pitch is P
Then, the pin rotation angle change amount η is as follows.

[0076]

(Equation 5)

FIG. 26 is a diagram showing the rotation angle variation η at each value of the pulley effective diameter (radius R ₀ ) using the link pitch P as a parameter.
m], the value of the rotation angle change η corresponding to the minimum value a of the effective pulley diameter (radius R ₀ ) is ηa,
The value of the rotation angle change amount η corresponding to the maximum value b of the effective pulley diameter is ηb.

Next, the optimum ratio of the center position on the X coordinate in the R shape of the pin end face will be described with reference to FIGS. 27, 28 and 29.

FIG. 27 is a view showing a state in which the center of the R shape of the pin end face is shifted in the X direction by a predetermined amount (that is, the shift amount a is changed) with respect to the pin rotation center 0, and the pin rotation angle θ is used as a parameter. FIG. 9 is a diagram showing a change in the X coordinate of a gap δ between the sheave and the sheave. In FIG. 27, the point where the gap δ becomes the minimum value is the contact point P (P
₁ , P ₂ , P ₃ ), and the change of the contact point P is the change amount μ of the pin width B (the longitudinal direction of the pin 26) due to the pin rotation, and is obtained from the δ value and the X value.

The improvement of noise when each divided pin bites into the sheave is as follows: 1) The difference between the values of e and d at the sheave biting position angle of the pin is reduced. 2) The change amount ε of the gap δ is reduced with respect to the change of the pin rotation θ. Further, the amount in the direction in which the pin width increases with respect to a change in θ is reduced as much as possible. Here, e: X value [mm] of the pin at the sheave biting position angle of the pin [d] Deviation of the pin thickness center with respect to the pin rotation center [m]
m] ε: Pin width change due to pin rotation (both sides) [μ]

FIGS. 28 and 29 show the above-mentioned pin width change amount ε at each pin rotation angle θ, using the amount of deviation a of the center of the R shape Rp of the pin end face with respect to the pin rotation center as a parameter. In the drawing, a link (plate) attachment angle f is set by a strength of the link or the like, and is a line perpendicular to the longitudinal line of the link (a line perpendicular to the straight line [X-axis] when the belt is in a straight line state). Z axis]) is the angle of the Y axis of each of the split pins 26a, 26b. When the belt is wound around the pulley, each link bends and each split pin is held integrally with the plate, so that it rotates by the same bending angle. Considering that the split pin 26b on the front side of the belt movement among the pair of split pins rotates leftward (positive direction), and the load transmitting contact between the pair of split pins moves in the positive direction of the Y axis. In general, the split pin 26b on the front side of the belt movement in the pair of split pins is attached to be inclined at a predetermined angle to the left (positive direction) beforehand. The split pin 26a on the rear side in the movement direction of the belt is mounted so that the link mounting angle is inclined at a predetermined angle to the right (negative direction), and the link plate 25 is mirror-symmetrical to the split pins 26b and 26a. And seated in the seat hole 30a.

FIG. 28 shows that the effective diameter of the pulley is the minimum diameter a, and the rotation angle change amount ηa at the minimum diameter a from the link mounting angle f is the usable rotation angle range of the pin. Note that FIG. 28 shows an R-shaped radius Rp = 10 [m] of the pin end surface.
m], and indicates the X coordinate at y ₀ = 0. FIG. 28
Therefore, in the pin rotation angle range ηa, the smallest pin width change amount is such that when the deviation amount a of the center of the radius Rp becomes the positive (+) rotation direction and the negative (−) rotation direction (positive value and negative value). It is understood that the points aA are located on the line aA between the displacement amounts 0 and an, and the point aA is calculated by a calculation formula such as linear interpolation or FIG.
Is read from the graph. At this time, the split pin 26b
Will rotate from the link mounting angle f in the straight state to the angle g in the negative direction (rightward), and the pin width change amount ε will be about 1.7 in both the forward rotation direction and the negative rotation direction. μ].

FIG. 29 is a view similar to FIG. 28 when the effective pulley diameter is the maximum diameter b. At the maximum diameter b, the rotation angle change amount η of the pin is ηb, and the rotation angle change amount ηb from the pin mounting angle f of the pin is the usable rotation angle range of the pin. At this time, the deviation amount aA corresponding to the smallest pin width change amount is the minimum value ηa of the pulley effective diameter maximum value a on the positive rotation side of the working rotation angle range.
In the same manner as in the case of the above, at the link mounting angle f, the pin width change amount is the same, and the shift amount a on the negative rotation side is
The amount of change in the pin width at A is substantially zero, and it has been confirmed that the optimum amount of deviation aA has no problem even with the maximum effective pulley diameter. At the maximum effective diameter, the split pin rotates from the link mounting angle f to a positive value h degrees.

Therefore, the optimum value of the shape of the pin end surface is an arc (R) shape at least on the X coordinate, and it is difficult to make the radius Rp of the R shape too small due to the strength due to Hertzian stress and the like. For this reason, it is desirable to be within the range of 5 to 15 [mm], and in the embodiment, it is approximately 10 [mm]. By making the pin end face R-shaped, the gap δ between the pin end face and the sheave due to the rotation angle of the pin, and therefore, the amount of change in the substantial pin width that comes into contact with the sheave at a predetermined rotation angle of the pin is extremely small. Fits in a small area. Further, the pin end face R
By shifting the shape and the center of the radius Rp (shift amount a), the curve drawn by the pin width change amount ε at each pin rotation angle θ has an extreme value downward (one side). Center of the arc (R) shape (shift a)
Is minimized by equally distributing to the positive rotation side and the negative rotation side so that the pin width change amount is minimized within the pin use rotation angle range, particularly at the minimum pulley effective diameter having a wide pin use rotation angle range. The value is determined, thereby obtaining the optimum shape of the pin end surface.

As an example, the minimum effective diameter of the pulley (the radius R ₀ from the center of the pulley to the pin center line y ₀ = ₀ ) a is 2
8.2 [mm], and the maximum effective diameter b of the pulley is 68.
When the link pitch P is 8 [mm], the rotation angle change ηa at the minimum effective diameter a is 8.1 [°], and the rotation angle change at the maximum effective diameter b is 8 [mm]. ηb is 3.3 [°]. When the link mounting angle f of the pin is 5 [°], the displacement aA corresponding to the minimum value (approximately 1.7 [μ]) of the pin width variation μ is 0.03.
[Mm]. At this time, the pin rotation angle g on the negative side (after the engagement of the pulleys) with the minimum effective pulley diameter is -3.1.
[°], and the pin rotation angle h on the negative rotation side (after pulley engagement) in the maximum effective pulley diameter is 1.7 [°].

Therefore, the displacement a is 0.2 [mm].
If set below, the pin width change amount can be kept within a range that does not cause much problem in practical use. Since the split pin 26a on the rear side in the moving direction of the link 25 has the link mounting angle in the (-) direction (the right rotation direction with respect to the Y axis), the displacement a is -0.2 [mm]. Therefore, the displacement a on the X coordinate is in the range of +0.2 to -0.2 [mm].

When the deviation of the radius Rp center (X coordinate) of the radius Rp of the pin end face from the pin rotation center 0 is zero, the pin width change within the pin rotation angle change range is determined by dividing the pin width change in the front of the belt moving direction. The pin 26b has a maximum at the pin rotation angle at the position where the belt starts to bite into the pulley (same as the pin link plate mounting angle), and has a small value at the pin rotation angle at which the belt rotates and the pin rotation ends. The pin width change amount is large within the pin rotation angle change range, but the deviation amount does not include 0, that is, the pin rotation center does not match the radius center (X coordinate) of the radius of the pin end face ( The direction of displacement is positive (rightward) or negative (leftward) with respect to the Y axis toward the pulley radius center, depending on the mounting angle of the link plate of the pin. Suppressed pins width variation to a small value in the rotation angle variation range. Therefore, the deviation amount is 0
(−0.2 <ah <0.2,
However, 0 is not included).

Next, with reference to FIG. 30 and FIG. 31, a loss caused by rotation of the pin itself when the pin bites into the sheave, that is, a so-called spin loss will be described. The spin loss is to minimize the value of the change in the pin width due to the pin rotation (both sides) ε [μ] × the X value e [mm] (see FIG. 27) at the pin sheave biting position angle. However, when it is difficult to improve the spin loss with the above-described noise improvement, it is better to give priority to the noise improvement.

FIGS. 30 and 31 are diagrams showing the biting position on the X coordinate at each pin rotation angle θ [°], using the amount of deviation a [mm] of the center of the R-shaped end face of the pin as a parameter. FIG. 30 shows a case where the pulley effective diameter is the minimum diameter a,
FIG. 31 shows a case where the pulley effective diameter is the maximum diameter b. In both figures, the radius Rp of the R-shaped end face of the pulley is 10 [m
m] and is obtained from the X coordinate at y ₀ = 0.

In FIG. 30, where the effective diameter of the pulley (the pulley radius R ₀ to the pin rotation center) is the minimum diameter a, the pin rotation angle change amount η in the use range based on the pin link mounting angle f is shown.
a (see FIG. 26), when the displacement amount is aA, the pin biting position e is about -0.13 [mm] on the positive (+) rotation side of the pin rotation angle θ (the link mounting angle f). Yes,
Approximately 0.12 [m] on the negative (-) rotation side (g; negative value)
m]. In FIG. 31 in which the pulley effective diameter R ₀ is the maximum diameter b, the pin biting position e is determined by the pin rotation angle change amount ηb in the usage range based on the pin link mounting angle f and the deviation amount aA. It is about -0.13 [mm] on the positive (+) rotation side (the link mounting angle f) of the angle θ, and is -0.03 on the negative (-) rotation side (h; positive value).
03 [mm].

Therefore, when the effective diameter of the pulley is the minimum a, the spin loss value (ε × e) is from ε × (0.012) to ε ×
(-0.13), and when the effective pulley diameter is the maximum, ε
× (−0.03) to ε × (−0.13). Specifically, the link mounting angle f = 5 [°], the displacement aA of the center of the pin end surface R shape radius Rp aa = 0.03 [mm], the minimum effective pulley diameter a = 28.2 [mm], and the minimum effective Use rotation angle change amount ηa = 8.1 [°] in diameter, pin rotation angle g =
−3.1 [°], maximum effective pulley diameter b = 68.8 [m]
m], the used rotation angle change amount ηb at the maximum effective diameter = 3.
3 [°] and the pin rotation angle h = 1.7 [°].

The spin loss value based on the pin biting position e is a satisfactory range in design. Therefore, from the viewpoint of the improvement of the spin loss, the pin end surface shape (Rp = 1)
0 [mm], the deviation a = 0.03 [mm]) is the optimum shape, and the radius Rp of the end face of the pin is Rp = 5 to 5.
15 [mm] and deviation amount a <| 0.2 | (however, not including 0) [mm] are appropriate shapes that are acceptable in design.

Next, the operation of the transmission endless belt 21 will be described. As shown in FIG.
When one bites into the pulley, a pair of split pins 26a, 26b
Moves relative to each other while contacting the rolling surfaces 31a,
Each rank G of the link chain 32 is bent,
Each of the blocks 22 and 23 swings with respect to the pin, and the first and second blocks 22 and 23 move relative to each other so as to align with the side surfaces of the sheave while contacting the projections 41 thereof. As a result, each split pin 26a, 26b and each block 22,
23 is curved along the effective diameter of the pulley device, that is, along the pitch line (circle) PP, but in this case, each block does not necessarily face the center axis of the pulley.

As described above, even if the blocks 22 and 23 bite obliquely with respect to the radial direction (the Y-axis) and the X-axis and the Z-axis due to the accuracy and deformation of the blocks and the sheaves, the respective blocks are not affected. Since the outer surface thereof contacts the sheave side surface only at the protruding surface 45 near the pitch circle, the split pins 26a and 26b contact the sheave side surface, so that one pitch (1 Rank G ...)
, The projecting outer surface 45 of the second block 23, one of the split pins 26b, the other split pin 26a, and the first
Projecting outer surface 45 of the block 22 sequentially contacts the sheave side surface. Therefore, for example, if each of the blocks 22 and 23 is (Y
Even if it is inclined (with respect to the axis, X axis, and Z axis), it is dispersed at four positions with respect to one pitch of the link chain and starts to bite into the pulley, and the biting pitch becomes smaller, and the polygonal effect is reduced. As a result, the sound generated when the pulley is caught has a high frequency and the sound energy is reduced, so that the generated noise can be reduced.

When the pins 26a and 26b bite into the pulley, as described above, the divided pins 26a and 26b roll on each other on the rolling surface 31a, so that the preceding pin 26b bites radially inward of the pulley. become. In this state, when both outer end surfaces 6c are flat in the front-rear direction (longitudinal direction of the belt) as in the conventional pin 6, the pin outer surface 6c
The relative gap between the pin and the sheave side surface changes, and the pin engagement start position shifts. That is, as shown in FIGS. 13 to 16, a pin having a flat end face (flat face) (even if there is a round shape in the radial direction (Y direction), X
The same applies to those that are flat in the direction, which is included in this). When the endless belt bites into the pulley, the spin of the pin causes the substantial width of the pin (the relative gap between the pin end face and the sheave) to change greatly. Then, the contact position (circumferential direction; X direction, radial direction; Y direction) of the pin with the sheave changes, and the polygon effect and the sliding between the pin and the sheave, particularly the radial sliding, increase. As a result, the relative width between the protruding outer side surface 45 of each of the blocks 22 and 23 that comes into contact with the sheave and the pin is also changed, and the polygonal effect is increased.
In addition to causing noise, the load on sheaves, blocks, and pins increases, which adversely affects the durability of the belt-type continuously variable transmission.

On the other hand, the end face of the pin according to the present invention has an R-shape at least in the X direction, and the center of the R-shape radius Rp deviates from the pin rotation center by a predetermined amount aA. The pin has a small change in the width of the pin, and when the pin is engaged with the pulley, the pin rotates.However, the change in the pin width is small, and the pitch of the pin end face into the sheave is constant. By keeping the polygon effect small, noise generation is reduced, and the influence of the rotation angle of the pin on the sheave and the influence on the block are reduced, thereby improving the durability of the belt-type continuously variable transmission. Improved, and reduced pin spin loss,
Transmission efficiency can be improved.

Further, when the belt 21 bites into the pulley,
As shown in FIG. 3, the opposite surface 31b of the pins 26a, 26b
And the contact positions of the concave grooves 40 of the blocks 22 and 23 are slightly shifted from the pitch circle PP in the outer diameter direction. As a result, in each of the blocks 22 and 23, a force in the direction of the arrow p is applied to a position shifted from the center position (front-back direction) of the entire block by the projecting outer surface 45 abutting on the sheave side surface, and a moment is applied to the block. Works, but the pin 26
The moment acting on the block is canceled by receiving the force in the direction of arrow q from the contact position with the a and 26b, and the inclination of the block in the radial direction is reduced.

In the above embodiment, the description has been made such that the protruding outer surfaces 45 of the two blocks 22 and 23 and the split pins 26a and 26b start to contact the sheave side surfaces at equal intervals at one pitch. , Actually the pin outer end surface 26
The shape is slightly shifted due to the round shape of c, and further, the shape is designed so as to start contact at unequal intervals, and by changing the frequency, white noise is obtained to improve quietness.

Further, in this embodiment, the endless belt having the first and second blocks 22 and 23 sandwiched between the pins 26 has been described. However, the shape of the pin end face according to the present invention is as follows.
Not limited to this, for example, Lu in which only the pin contacts the sheave
The same can be applied to the K-type endless belt, and further to all the endless belts in which the pin contacts the sheave side. Further, the pin is preferably applied to the above-mentioned split pin, but is not limited thereto.
As disclosed in Japanese Patent Application Laid-Open No. 8-49746, the present invention can be applied to a single pin having a rolling surface between a link (plate) and a key. The invention can be applied to endless belts having moving pins.

[Brief description of the drawings]

FIG. 1 is a diagram showing a conventional transmission endless belt,
(A) is a side view of a partial section [BB, CC section of (b)], and (b) is an AA section of (a).

FIG. 2 is a side view showing an endless transmission belt according to the present invention.

FIG. 3 is an enlarged side view showing a portion where the pulley bites.

FIG. 4 is a front sectional view thereof.

FIG. 5 is a plan view thereof.

FIGS. 6A and 6B are diagrams showing parts of the endless transmission belt according to the present invention, wherein FIGS. 6A and 6B show blocks, FIG. 6C shows link plates, and FIGS. 6D and 6E show spring means. Is shown.

FIGS. 7A and 7B are enlarged views showing a block, in which FIG. 7A is a cross-sectional view taken along the line AA in FIG.

FIGS. 8A and 8B are enlarged views showing a split pin, where FIG. 8A is a side view, FIG. 8B is a front view, and FIG. 8C is a cross-sectional view taken along line CC of FIG.

FIG. 9 is a side view of a pin end face for analyzing a change in clearance (gap) with a sheave due to rotation of the pin.

FIG. 10 is a diagram schematically showing an enlarged scale of a cross section of the pin end surface in the X direction (circumferential direction).

FIG. 11 is a diagram schematically showing an enlarged scale of a cross section of the pin end surface in the Y direction (radial direction).

12A and 12B show a case where the R shape of the end face of the pin is inclined at X and Y coordinates, where FIG. 12A shows the Y direction (radial direction) and FIG.
FIG. 3 is a diagram showing an X direction (circumferential direction).

FIG. 13 shows a gap between the pin and the sheave in the Y direction.
FIG. 4 is a diagram showing a pin rotation angle as a parameter, showing a case where a pin end surface shape is flat and a pulley effective diameter is a minimum diameter.

FIG. 14 is a view showing a case where the shape of the pin end surface is flat and the effective diameter of the pulley is the maximum diameter.

FIG. 15 shows a clearance between the pin and the sheave in the X direction.
FIG. 4 is a diagram showing a pin rotation angle as a parameter, showing a case where a pin end surface shape is flat and a pulley effective diameter is a minimum diameter.

FIG. 16 is a diagram showing a case where the shape of the pin end surface is flat and the effective diameter of the pulley is the maximum diameter.

FIG. 17 shows a gap between the pin and the sheave in the X direction.
FIG. 5 is a diagram showing a pin rotation angle as a parameter, showing a case where the pin end surface shape is a round shape, the center of the round shape coincides with the pin rotation center on the X axis, and y ₀ = 0 and the pulley effective diameter is the minimum.

FIG. 18 is a diagram showing values on the X-axis shifted 1.5 [mm] upward in the Y direction.

FIG. 19 is a diagram showing values on the X-axis shifted 1.5 [mm] downward in the Y direction.

FIG. 20 is a diagram showing a case where the center of the R shape of the pin end face is shifted to the right (positive direction) by a predetermined amount on the X-axis with respect to the center of rotation of the pin and the pulley effective diameter is the minimum diameter.

FIG. 21 is a diagram showing a case where the center of the R shape of the pin end face is shifted to the left (negative direction) by a predetermined amount on the X-axis with respect to the pin rotation center and the pulley effective diameter is the minimum diameter.

FIG. 22 is a view similar to FIG. 17 when the pulley effective diameter is the maximum diameter.

FIG. 23 is a view similar to FIG. 20 when the effective pulley diameter is the maximum diameter.

FIG. 24 is a view similar to FIG. 21 when the pulley effective diameter is the maximum diameter.

FIG. 25 is a schematic diagram showing a state when the endless belt bites into a pulley.

FIG. 26 is a diagram illustrating a relationship between a pulley effective diameter and a rotation angle change amount using a link pitch as a parameter.

FIG. 27 is a diagram showing a change in clearance from a sheave due to pin rotation as a parameter of a pin rotation angle, and is an explanatory diagram for obtaining a pin width change amount.

FIG. 28 is a diagram showing a pin width change amount according to a pin rotation angle using a shift amount a of the center of the R shape of the pin end surface as a parameter, showing a case where the pulley effective diameter is the minimum diameter.

FIG. 29 when the pulley effective diameter is the maximum diameter.
FIG.

FIG. 30 is a view showing a biting position according to a pin rotation angle using a shift amount of the center of the R shape of the pin end surface as a parameter, and shows a case where the pulley effective diameter is the minimum diameter.

FIG. 31 when the pulley effective diameter is the maximum diameter.
FIG.

[Explanation of symbols]

Reference Signs List 21 endless belt for transmission 22 first block 23 second block 25 link plate 26 pin 26a, 26b split pin 26c outer end surface 30a seat hole 32 link chain 35 through hole 40 concave groove 45 protruding outer surface Rp radius radius δ skimmer (Gap) a The amount of deviation of the radius of the radius of the pin end face with respect to the center of rotation of the pin f The mounting angle of the link plate of the pin aA The appropriate amount of deviation θ Pin rotation angle 0 Center of rotation of pin ε Pin width change

Claims (12)

[Claims] 1. An endless transmission belt comprising: a number of pins having rolling surfaces; and a number of link plates that are alternately connected by these pins to form a link chain. The outer end surface has a shape and a length that can contact the sheave side surface of the pulley, and the end surface shape of the pin has a curved shape at least in the X direction with the longitudinal direction of the endless belt as the X direction. Endless belt for transmission. 2. The transmission endless belt according to claim 1, wherein an end surface shape of the pin is a substantially cylindrical shape having a curved shape in the X direction. 3. The transmission endless belt according to claim 1, wherein the pins comprise a pair of split pins having rolling surfaces that can abut each other. 4. The curved shape has a radius of 5 to 15
The endless belt for transmission according to any one of claims 1 to 3, wherein the belt has a round shape having a range of [mm]. 5. The end face shape of the split pin is obtained by calculating the pin width change amount obtained from the gap between the pin end face and the sheave in the X direction by the rotation angle change amount in a pin use range. The endless transmission belt according to claim 4, further comprising a shift amount of a radius center of the round shape with respect to the center of rotation of the pin in the X direction, which is determined by equally distributing the rotation to the positive rotation side and the negative rotation side. 6. The amount of deviation is from −0.2 to +0.2 [m
m]. The transmission endless belt according to claim 5, wherein 7. The transmission endless belt according to claim 6, wherein the deviation amount is a value not including 0. 8. The pair of split pins are seated on seat holes formed in the link plate on a side opposite to the rolling surface and attached to the link plate, and the endless end of the pair of split pins is provided. A split pin on the front side in the movement direction of the belt is attached to the link plate at a predetermined value in a forward rotation direction with respect to a Y direction orthogonal to the X direction, with the rotation in the endless belt movement direction being a forward rotation. An endless transmission belt according to any one of claims 5 to 7. 9. The transmission for transmission according to claim 8, wherein the front split pin has a predetermined radial deviation of the radius center of the round shape from the center of rotation of the pin behind the moving direction of the endless belt. Endless belt. 10. The radius of the radius is approximately 10
[Mm], and the predetermined deviation amount is approximately 0.03 [m
m]. The endless belt for transmission according to claim 9. 11. At least one block which is sandwiched between the pins adjacent in the X direction and has a through hole penetrating the link chain in the X direction, wherein the block has both left and right sides 10. A protruding outer surface having a shape protruding in the left-right direction and having a shape capable of contacting the sheave side surface of the pulley, at a position on the outer surface substantially corresponding to the outer end surface of the pin. Endless belt for transmission according to the above. 12. The block comprises a first and a second block having a projection which can come into contact with each other in the X direction and a concave groove for receiving the split pin on the opposite side, wherein the pitch of the link chain is one pitch. The endless belt for transmission according to claim 11, wherein a total of four locations of the outer end faces of the pair of split pins and the projecting outer faces of the first and second blocks are sequentially contacted with the sheave side face.