JP2011075089A - Element of belt type continuously variable transmission and method for manufacturing the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an element of a belt type continuously variable transmission capable of promoting increase of a contact area between a side surface of the element and a pulley by shortening time required for removing an oil film for achieving improvement of frictional force. <P>SOLUTION: The belt type continuously variable transmission includes an input-side pulley 1 with its groove width variable in the input shaft direction, an output-side pulley 2 with its groove width variable in the output shaft direction, and a belt (a belt V for the continuously variable transmission) hung over between the input-side pulley 1 and the output-side pulley 2. The belt V is made of a large number of plate-like elements 4 laminated in the plate-thickness direction and bundled by an endless band (a laminated ring 3). In the belt type continuously variable transmission, recesses 41 and projections 42 are formed on the side surface (a flank surface 4a) of the plate-like element 4 in a direction (a direction of an arrow Y) orthogonal to the plate-thickness direction (a direction of an arrow X) over the overall length from one end 4a1 to the other end 4a2. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a plate-like element constituting a belt stretched around a pulley in a belt type continuously variable transmission and a method for manufacturing the same.

  Conventionally, an input side pulley having a variable groove width on the input shaft, an output pulley having a variable groove width on the output shaft, and a belt spanned between the input side pulley and the output side pulley are provided. In a continuously variable transmission in which a large number of plate-like elements are stacked in the plate thickness direction and bundled by an endless band, the belt is a groove in the plate thickness direction that discharges lubricating oil to the pulley circumferential direction on the side surface of the plate-like element. Is known (see, for example, Patent Document 1).

JP 2007-303520 A

  However, in the element of the conventional belt type continuously variable transmission, the groove formed on the side surface of the plate-like element is the groove in the plate thickness direction. For this reason, there is a problem that the lubrication oil discharge rate is slow, the time required for oil film removal is lengthened, and the increase in the contact area between the element side surface and the pulley sheave surface is delayed, so that the margin for improving the frictional force is suppressed. there were.

  That is, when the element side surface and the sheave surface of the pulley come into contact, lubricating oil is sealed in the groove, and an oil film gap is formed between the element side surface and the sheave surface of the pulley. The lubricating oil sealed in the groove has an action of discharging the lubricating oil, after flowing in the direction of the oil film gap, changing the flow direction to the centrifugal force direction and moving through the oil film gap. Therefore, only the cross-sectional area of the oil film gap becomes the effective flow path cross-sectional area for oil film removal, and if the oil film gap becomes narrow, the flow rate of the lubricating oil decreases and the oil film removal time is prolonged.

  The present invention has been made paying attention to the above problem, and by shortening the time required for oil film removal, it is possible to promote an increase in the contact area between the side surface of the element and the pulley and to improve the frictional force. It is an object of the present invention to provide a belt-type continuously variable transmission element and a method for manufacturing the same.

In order to achieve the above object, in the belt-type continuously variable transmission of the present invention, an input pulley having a variable groove width in the input shaft direction, an output pulley having a variable groove width in the output shaft direction, and an input side And a belt stretched between the pulley and the output-side pulley. The belt was obtained by stacking a large number of plate-like elements in the thickness direction and bundling them with an endless band.
In this belt type continuously variable transmission, a concave portion and a convex portion are formed on the side surface of the plate-like element over the entire length from one end to the other end in a direction perpendicular to the plate thickness direction.

Therefore, a concave portion and a convex portion are formed on the side surface of the plate-like element of the belt-type continuously variable transmission according to the present invention over the entire length from one end to the other end in a direction perpendicular to the plate thickness direction.
Therefore, the concave portion and the convex portion coincide with the centrifugal force direction when the pulley of the continuously variable transmission rotates. For this reason, when the lubricating oil supplied to the inside of the contact portion between the side surface of the element and the pulley shows the discharging action of the lubricating oil that escapes outward according to the centrifugal force due to rotation, it is formed between the convex portion and the pulley. The total cross-sectional area obtained by adding the cross-sectional area of the dent space due to the recess to the cross-sectional area of the oil film gap is the effective channel cross-sectional area for oil film removal.
That is, compared with the case where only the cross-sectional area of the oil film gap is used as the effective flow path cross-sectional area for removing the oil film, the effective flow path cross-sectional area is increased, and the amount of lubricating oil discharged is increased. Due to the increase in the discharge amount, the oil film is quickly removed, and the side surface of the element and the pulley come into contact with the removal of the oil film, thereby promoting the increase in the contact area between the side surface of the element and the pulley.
In this way, by shortening the time required to remove the oil film, the contact area between the element side and the pulley is increased, resulting in increased transmission torque capacity, improved belt torque transmission efficiency, improved fuel efficiency, and smaller transmission It is possible to achieve an improvement in friction force (friction coefficient) that is useful for the conversion to the like.

It is a perspective view which shows two sets of pulleys of the maximum deceleration state with the belt-type continuously variable transmission which applied the element of Example 1 to the belt. It is an expansion perspective view which shows a part of belt for continuously variable transmission to which the element of Example 1 is applied. It is a front view of the element of the belt type continuously variable transmission of Example 1. It is a figure which shows the principal part of the element of the belt-type continuously variable transmission of Example 1, (a) shows the side view of an element, (b) shows the enlarged view of the element flank part F of FIG. It is explanatory drawing which shows the direction of the centrifugal force in the state which the element of the belt-type continuously variable transmission of Example 1 is rotating, contacting a pulley. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an enlarged view showing a plurality of rows of concave grooves and ridges formed on a flank surface of an element of a belt type continuously variable transmission of Embodiment 1, and (a) shows an enlarged view of the flank surface viewed from a centrifugal force direction. (B) shows an enlarged view when one concave groove is viewed from the centrifugal force direction. It is explanatory drawing which shows the element manufacturing method in Example 1, (a) shows a raw material conveyance process, (b) shows a raw material setting process, (c) shows a punching process, (d) shows an element moving process (E) shows the groove processing step, (f) shows the flattening treatment step, and (g) shows the element discharging step. It is explanatory drawing which shows the element manufactured in Example 1, (a) shows an element perspective view, (b) shows the front view of an element flank part, (c) is the arrow D of FIG. 8 (a). The sagging occurrence part by the punching seen from the direction is shown. It is explanatory drawing which shows the contact relationship of the two flank surfaces in the element of the belt-type continuously variable transmission of Example 1, and the two sheave surfaces in a pulley, (a) The angle (beta) which two flank surfaces make, and two sheaves The relationship between the angles α formed by the surfaces is shown, and (b) shows the contact pressure distribution characteristics acting between the flank surface and the sheave surface. It is explanatory drawing which shows the lubricating oil discharge | emission comparison effect | action of the element of a comparative example, and the element of Example 1, (a) shows the lubricating oil discharge | emission effect | action in the element of a comparative example, (b) is lubrication in the element of Example 1. Shows oil draining action. It is explanatory drawing which shows the contact area contrast effect | action of the belt-type continuously variable transmission using the element of the comparative example, and the belt-type continuously variable transmission using the element of Example 1, (a) is the contact area in a low gear ratio. The contrast action is shown, and (b) shows the contact area contrast action at the high gear ratio. It is explanatory drawing which shows the element manufacturing method in a comparative example, (a) shows a raw material conveyance process, (b) shows a raw material setting process, (c) shows a punching process. It is explanatory drawing which shows the element manufactured by the comparative example, (a) shows an element perspective view, (b) shows the front view of an element flank part, (c) is the arrow C direction of FIG. 8 (a). This shows the sagging occurrence part due to punching as seen from. It is a figure which shows the principal part of the element of the belt-type continuously variable transmission of Example 2, (a) shows the side view of an element, (b) shows the enlarged view of an element flank part.

  Hereinafter, the best mode for realizing an element of a belt type continuously variable transmission according to the present invention will be described based on Example 1 and Example 2 shown in the drawings.

First, the configuration will be described.
FIG. 1 is a perspective view showing two sets of pulleys in a maximum deceleration state in a belt-type continuously variable transmission in which the element of Embodiment 1 is applied to a belt. FIG. 2 is an enlarged perspective view showing a part of a continuously variable transmission belt to which the element of the first embodiment is applied. FIG. 3 is a front view of elements of the belt type continuously variable transmission according to the first embodiment. 4A and 4B are diagrams showing the main part of the element of the belt type continuously variable transmission according to the first embodiment. FIG. 4A is a side view of the element, and FIG. 4B is an enlarged view of the element flank portion F of FIG. Indicates.

  The continuously variable transmission belt V to which the element of the belt type continuously variable transmission of the first embodiment is applied is stretched between the input side pulley 1 and the output side pulley 2 as shown in FIG. Here, the torque from the engine (not shown) is transmitted to the input pulley 1 through a torque converter and a forward / reverse switching mechanism, and the reduction gear (not shown) from the output pulley 2 via the continuously variable transmission belt V. And it is transmitted to the tire through the drive shaft. The input-side pulley 1 has a fixed pulley 11 and a slide pulley 12, and the groove width is variable in the input shaft direction. The output pulley 2 has a fixed pulley 21 and a slide pulley 22, and the groove width is variable in the output shaft direction. The pulleys 11, 12, 21, and 22 are formed with sheave surfaces 11a, 12a, 21a, and 22a in contact with the continuously variable transmission belt V. The slide pulleys 12 and 22 generate a pressing force in the direction of pinching the belt by piston hydraulic pressure.

  As shown in FIG. 2, the continuously variable transmission belt V is formed of a laminated ring (endless band) 3 in which a large number of annular rings are stacked from the inside to the outside, a plate material, and two sets of pulleys 1, And a plate-like element 4 having a flank surface 4a in contact with the two sheave surfaces 11a, 12a, 21a, 22a.

  The laminated ring 3 is formed by welding a thin plate of the highest strength material equivalent to maraging steel having a thickness of about 0.2 mm to form an annular ring, and laminating a plurality of annular rings having slightly different diameters from inside to outside. Consists of.

  As shown in FIG. 2, the continuously variable transmission belt V includes two sets of laminated rings 3, 3 on both sides of the saddle grooves 4b, 4b of the elements 4,. And is configured by bundling these many elements 4. Then, when torque is transmitted with the continuously variable transmission belt V sandwiched between the two sets of pulleys 1 and 2, the laminated ring 3 supports the force that the element 4 tries to spread in the outer diameter direction. The element 4 supports the pressing force from the pulleys 1 and 2.

  The element 4 is formed of a steel plate having a thickness of about 2 mm. As shown in FIG. 3, the flank surfaces 4a and 4a, saddle grooves 4b and 4b, a neck portion 4c, a nose portion 4d, and an ear portion 4e, 4e, a hole portion 4f, and a locking edge portion 4g.

  The flank surfaces 4a and 4a are formed on both sides of the element in contact with the sheave surfaces 11a, 12a, 21a and 22a of the pulleys 1 and 2, respectively. The saddle grooves 4b and 4b are formed at an element inner position where two sets of laminated rings 3 and 3 are sandwiched from both sides. The neck portion 4c is formed at the center position of the element sandwiched between the saddle grooves 4b and 4b. The nose portion 4d is formed to protrude in the belt traveling direction at the upper portion of the element front position. The ear portions 4e and 4e are formed extending from the nose portion 4d in the element width direction. The hole portion 4f is formed below the element back surface position corresponding to the set position of the nose portion 4d. The locking edge portion 4g is formed in the width direction at the element front position having the flank surfaces 4a, 4a.

  The flank surfaces 4a and 4a of the element 4 are concave portions extending in a direction (indicated by an arrow Y) perpendicular to the plate thickness direction (indicated by an arrow X) of the element 4 as shown in FIG. 4 (a). 41 and the convex part 42 were formed. Here, as shown in FIG. 4B, the concave portion 41 and the convex portion 42 are formed over the entire length from one end (lower end) 4a1 to the other end (upper end) 4a2 of the flank surface 4a, and alternately in the thickness direction. Arrange on the pitch.

  The concave portion 41 is a concave groove that discharges lubricating oil in the radial direction of the pulleys 1, 2, that is, in the direction of centrifugal force generated by the rotation of the pulleys 1, 2, and the convex portion 42 includes two sets of pulleys 1, 2. This is a ridge that contacts the sheave surfaces 11a, 12a, 21a, 22a via an oil film.

  FIG. 5 is an explanatory diagram showing the direction of centrifugal force when the element of the belt-type continuously variable transmission according to the first embodiment rotates while contacting the pulley. FIG. 6 is an enlarged view showing a plurality of rows of grooves and ridges formed on the flank surface of the element of the belt type continuously variable transmission according to the first embodiment. FIG. 6A shows the flank surface viewed from the centrifugal force direction. An enlarged view is shown, (b) shows an enlarged view when one groove is viewed from the centrifugal force direction. Note that the “centrifugal force direction” shown in FIG. 6 represents the tip in the centrifugal force direction indicated by a one-dot chain line arrow in FIG.

  As shown in FIG. 5, for example, when the fixed pulley 11 rotates counterclockwise, a centrifugal force is generated from the center O of the fixed pulley 11 toward the outer diameter direction as indicated by a one-dot chain line arrow. On the other hand, the element 4 rotates at high speed on an arc along the fixed pulley 11 with the flank surface 4a facing the sheave surface 11a. At this time, the plate thickness direction of the element 4 coincides with the traveling direction of the element 4, and the direction perpendicular to the plate thickness direction of the element 4 coincides with the centrifugal force direction generated by the rotation of the fixed pulley 11.

  That is, the concave portion 41 and the convex portion 42 formed in a direction perpendicular to the plate thickness direction of the element 4 coincide with the direction of the centrifugal force generated by the rotation of the fixed pulley 11. 5 shows only the relationship between the sheave surface 11a of the fixed pulley 11 and the element 4 in the input-side pulley 1, the relationship between the other pulleys 12, 21, 22 and the element 4 is the same.

  Further, the cross-sectional area S between the fixed pulley 11 and the sheave surface 11a is, as shown in FIG. 6, the cross-sectional area S1 of the oil film gap Y formed in the region between the convex portion 42 and the sheave surface 11a (FIG. (b) indicated by a thin dot) and a cross-sectional area S2 (indicated by a dark dot in FIG. 6B) of the inner region of the recess 41.

Assuming that the pitch interval of the recesses 41 is amm, the pitch interval of the projections 42 is amm, the shape of the recesses 41 is an arc waveform having a radius a / 4 mm, and the interval between the flank surface 4a and the sheave surface 11a is bmm. Area S is
S = S1 + S2
= (A × b) + (a / 2) ²
It can obtain | require by the type | formula.

Next, the manufacturing method of the element 4 of Example 1 is demonstrated.
FIG. 7 is an explanatory view showing an element manufacturing method in Example 1, (a) showing a material conveying step, (b) showing a material setting step, (c) showing a punching step, (d) Represents an element moving process, (e) represents a groove machining process, (f) represents a planarization process, and (g) represents an element discharging process. 8A and 8B are explanatory views showing the element manufactured in Example 1, wherein FIG. 8A is an element perspective view, FIG. 8B is an element flank portion, and FIG. 8C is an arrow in FIG. The sagging occurrence part by the punching seen from D direction is shown.

  As shown in FIG. 7, the element 4 of the first embodiment includes a female die 101, a male punch 102, a plate presser 103 disposed at a position facing the die 101, and a position facing the punch 102. It is manufactured by a press working apparatus 100 having a fine plate blanking process in which a steel plate material W is sheared and punched by relative movement of a die 101 and a punch 102.

  Here, the fine blanking process is a method of punching by controlling the material flow in the sheared portion of the steel sheet material W to be punched. That is, the die 101 and the punch 102 having extremely small clearance, the plate presser 103 having the knife-edge-shaped V ring and the plate holder 104 generate a high compressive stress inside the steel plate material W, thereby increasing the ductility of the steel plate material W. In this way, the occurrence of cracks is prevented, and a shear surface without breakage is obtained.

  In the material conveying step, as shown in FIG. 7A, the steel sheet material W is conveyed to the press working apparatus 100 from a direction perpendicular to the punching direction (shear direction) (horizontal direction).

  In the material setting step, as shown in FIG. 7B, the steel plate material W conveyed to the press working apparatus 100 is restrained by closing the die 101, the punch 102, the plate presser 103, and the plate support 104. At this time, hydraulic pressure is applied to the plate holder 103 and the plate holder 104, and a knife-edge V ring (not shown) formed on the plate holder 103 is driven into the steel plate material W. And the steel plate material W which is going to spread in the direction perpendicular to the punching direction (horizontal direction) is pressed down to increase the compressive stress of the steel plate material W to be punched.

  In the punching process, as shown in FIG. 7 (c), the outline of the element 4 is punched from the steel plate material W constrained by the material setting process by fine blanking. At this time, the positions of the punch 102 and the plate holder 104 are fixed, and the die 101 and the plate presser 103 are lowered. As a result, the relative positions of the die 101 and the punch 102 are shifted to form a shear plane. In addition, a curved portion 106 called “sag” is generated on the shear cut surface of the steel sheet material W.

  In the element moving step, as shown in FIG. 7 (d), the punching element 4 ′ from the punching step is relatively moved to the groove processing position in the punching direction while being sandwiched between the punch 102 and the plate holder 104. At this time, the positions of the punch 102 and the plate holder 104 are fixed, and the die 101 and the plate presser 103 are lowered.

  In the grooving step, as shown in FIG. 7 (e), the grooving tool 105 set on the plate retainer 103 is pressed against both side portions of the punching element 4 ′ that has been relatively moved, and the shapes of the concave portion 41 and the convex portion 42 are formed. The concave portion 41 and the convex portion 42 are formed by coining processing for marking (compression transfer). Note that the surface of the groove processing tool 105 has a reverse shape of the concave portion 41 and the convex portion 42. At this time, since the punch 102 is retracted upward, a bulge 107 is generated in the plate thickness direction on both sides of the punching element 4 ′ with coining.

  In the flattening process, as shown in FIG. 7 (f), the bulging 107 in the plate thickness direction of the plate-like element 4 is flattened by a punch 102 and a plate holder 104 by coining. At this time, the punch 102 retracted upward is lowered.

  In the element discharging process, as shown in FIG. 7 (g), the plate-like element 4 is released from the restriction by the die 101, the punch 102, the plate retainer 103, and the plate holder 104, and the groove processing and flattening processing are completed. The element 4 is discharged.

  Thus, the plate-shaped element 4 forms the recessed part 41 and the convex part 42 formed in the flank surface 4a of both sides in the post-process of fine blanking.

  Further, as shown in FIG. 8 (c), by performing groove processing and flattening processing by coining processing, the curved portion 106 (sag) of the shear cut surface of the steel sheet material W generated during fine blanking processing is obtained. , Corrected to almost right angle.

Next, the operation will be described.
First, the “characteristics of the belt type continuously variable transmission” will be described, and then the actions of the elements of the belt type continuously variable transmission of the first embodiment will be described as “lubricating oil discharging action”, “contact area increasing action”, The description will be divided into “characteristic actions in the manufacturing method”.

[Characteristics of belt type continuously variable transmission]
FIG. 9 is an explanatory view showing a contact relationship between two flank surfaces in the element of the belt type continuously variable transmission of the first embodiment and two sheave surfaces in the pulley, and (a) an angle β formed by the two flank surfaces. And (b) shows the contact pressure distribution characteristics acting between the flank surface and the sheave surface.

  In the continuously variable transmission, in order to increase the maximum transmission torque when the continuously variable transmission belt V is passed between the input side pulley 1 and the output side pulley 2, as shown in FIG. In addition, the angle β formed by the two flank surfaces in the element is made slightly larger than the angle α formed by the two sheave surfaces.

  Therefore, as shown in FIG. 9B, the contact pressure between the flank surface and the sheave surface increases as the upper portion of the flank surface (portion close to the saddle groove) is reached. That is, the oil film gap formed between the flank surface and the sheave surface becomes narrower toward the upper portion of the flank surface (portion close to the saddle groove).

  Therefore, when the lubricating oil flows in the pulley outer diameter direction due to the centrifugal force generated by the rotation of the pulley, the lubricating oil flowing through the oil film gap is less likely to flow toward the upper part of the flank surface (portion close to the saddle groove).

[Lubricating oil discharge effect]
FIG. 10 is an explanatory diagram showing the lubricating oil discharge action of the element of the comparative example and the element of the first embodiment. (A) shows the lubricating oil discharge action of the element of the comparative example, and (b) shows the first embodiment. The lubricating oil discharge | emission effect | action in this element is shown.

  In the element E of the comparative example, a plurality of grooves M in the thickness direction (perpendicular to the centrifugal force direction) are formed on the side surface E1. As a result, when the flank surface E1 which is the side surface of the element E and the sheave surface P1 of the pulley P come into contact with each other, the lubricating oil supplied to the inside of the contact portion is inside the groove M (indicated by dark dots in FIG. 10 (a)). ) And an oil film gap Y (indicated by a thin dot in FIG. 10A) is formed between the side surface E1 and the sheave surface P1.

  Here, the lubricating oil flows toward the pulley outer diameter side by the centrifugal force generated by the rotation of the pulley P. Therefore, the lubricating oil sealed in the groove M flows in the direction of the oil film gap Y, then moves in the oil film gap Y by changing the flow direction to the centrifugal force direction, and is discharged. Therefore, in the element E of the comparative example, only the cross-sectional area S1 of the oil film gap Y becomes an effective flow path cross section for discharging the lubricating oil and removing the oil film.

  On the other hand, in the element 4 of Example 1, the concave surface 41 and the convex portion 42 are formed on the flank surface 4a which is a side surface in a direction perpendicular to the plate thickness direction. Thereby, for example, when the flank surface 4a of the element 4 and the sheave surface 11a of the fixed pulley 11 come into contact, the lubricating oil supplied to the inside of the contact portion is shown inside the recess 41 (indicated by dark dots in FIG. 10 (b)). ) And an oil film gap Y (indicated by thin dots in FIG. 10B) is formed between the convex portion 42 and the sheave surface 11a.

  Here, since the concave portion 41 and the convex portion 42 coincide with the direction of the centrifugal force, the lubricating oil sealed in the concave portion 41 is moved and discharged in the concave portion 41 by the centrifugal force generated by the rotation of the fixed pulley 11. The Further, the lubricating oil in the oil film gap Y is also moved and discharged in the oil film gap Y by centrifugal force.

  Therefore, in the element 4 of the first embodiment, the sum (S1 + S2) of the cross-sectional area S1 of the oil film gap Y and the cross-sectional area S2 of the recess 41 becomes an effective flow path cross section for discharging the lubricating oil and removing the oil film.

  Therefore, the effective channel cross-sectional area of the element 4 of the first embodiment is set to the effective channel cross-sectional area S2 of the concave portion 41 as compared to the case where only the cross-sectional area S1 of the oil film gap Y is set as the effective channel cross-sectional area. Can be enlarged by minutes.

Furthermore, the flow rate Q of the fluid is
Q = S (cross-sectional area) x V (speed)
It is calculated by the following formula.
Therefore, if it is assumed that V (velocity) is constant, it is understood that the flow rate Q increases as S (cross-sectional area) increases.

As described above, in the element E of the comparative example, the effective flow path cross-sectional area is only the cross-sectional area S1 of the oil film gap Y. Therefore, the flow rate Q1 in the element E of the comparative example is
Q1 = S1 × V
It is calculated by the following formula.

On the other hand, in the element 4 of the first embodiment, the effective flow path cross-sectional area is the sum (S1 + S2) of the cross-sectional area S1 of the oil film gap Y and the cross-sectional area S2 of the concave portion 41. Q2 is
Q2 = (S1 + S2) × V
It is calculated by the following formula.

As described above, the element 4 of Example 1 has a shape in which the flow rate (discharge amount) of the lubricating oil is increased and the lubricating oil is easily removed by the cross-sectional area S2 of the recess 41. For example, assuming that the shape of the recess 41 is an arc waveform having a radius of a / 4 mm, the cross-sectional area S2 = (a / 2) ² , and in the element 4 of Example 1, the flow rate of the lubricating oil is (a / 2). ) Increase by ² minutes.

の式により求められる（なお、Ｔ_０は比較例のエレメントＥにおける潤滑油排出時間）。 As a result of increasing the flow rate (discharge amount) of the lubricating oil in this way, assuming that the same amount of lubricating oil is discharged, the lubricating oil discharge time T ₁ in the element 4 of Example ₁ is:

(T ₀ is the lubricating oil discharge time in the element E of the comparative example).

  Therefore, when the same amount of lubricating oil is discharged, the time required for discharging the lubricating oil is shorter in the element 4 of Example 1 than in the element E of the comparative example, and the time required for removing the oil film is shortened. can do.

  Further, as described above, in the belt-type continuously variable transmission, the contact pressure between the flank surface and the sheave surface increases as the upper part of the flank surface (portion close to the saddle groove), and the oil film gap that flows in the pulley outer diameter direction The lubricating oil that flows through the top of the flank becomes more difficult to flow as it reaches the upper part of the flank surface (the part near the saddle groove).

  For this reason, in the element E of the comparative example in which only the cross-sectional area S1 of the oil film gap Y is the effective flow path cross-sectional area, it is assumed that it becomes difficult to discharge the lubricating oil as it becomes the upper part of the flank surface (the part close to the saddle groove). However, in the element 4 of the first embodiment, on the other hand, a flow path corresponding to the cross-sectional area S2 of the recess 41 can be secured regardless of the contact pressure between the flank surfaces 4a and 4a and the sheave surfaces 11a and 12a. . Therefore, in the element 4 of the first embodiment, it is possible to prevent the oil film removing action from being lowered and to reliably shorten the time required for oil film removal.

  Furthermore, in the element 4 of Example 1, the recessed part 41 and the convex part 42 are a plurality of rows of concave grooves and convex lines formed alternately in the plate thickness direction. Therefore, the effective flow path cross section for oil film removal can be enlarged, and oil film removal can be performed more rapidly.

[Contact area increasing effect]
FIG. 11 is an explanatory view showing the contact area contrasting effect of the belt type continuously variable transmission using the element of the comparative example and the belt type continuously variable transmission using the element of the first embodiment. The contact area contrast action in the ratio is shown, and (b) shows the contact area contrast action in the high gear ratio.

  In a belt type continuously variable transmission, a belt V for a continuously variable transmission spanned between an input side pulley 1 and an output side pulley 2 is partially a friction force (coefficient of friction) that exceeds a certain level with the pulleys 1 and 2. When the pulleys 1 and 2 come into contact with each other, the pulleys 1 and 2 rotate as the pulleys 1 and 2 rotate.

  Here, the magnitude of the frictional force (friction coefficient) is determined by the amount of lubricating oil between the element 4 and the pulleys 1 and 2, and if the amount of lubricating oil is large, the element 4 slips and no frictional force is generated. The state in which this frictional force (coefficient of friction) exceeds a certain level and the continuously variable transmission belt V rotates together with the pulleys 1 and 2 is referred to as a “belt-engaged state”, from the start of biting to the end of biting. Is the belt biting angle.

  In the continuously variable transmission belt V to which the element E of the comparative example is applied, the lubricating oil supplied to the inside of the contact portion between the belt V and the pulleys 1 and 2 is discharged by centrifugal force, and the element E and the pulleys 1 and 2 are discharged. When the amount of lubricating oil becomes appropriate and the element E is engaged with the pulleys 1 and 2, the engagement start position is A2 at the low transmission ratio and the C2 position at the high transmission ratio. The biting angles at this time are θ1 and θ2, respectively.

  On the other hand, in the continuously variable transmission belt V to which the element 4 of the first embodiment is applied, the oil film can be quickly removed as described above, so that the friction between the pulleys 1 and 2 and the belt V exceeds a certain level. Contact with force (coefficient of friction) can be started quickly. That is, in the continuously variable transmission belt V to which the element 4 of the first embodiment is applied, the biting start position of the element 4 is A1 at the low gear ratio and the C1 position at the high gear ratio. The biting angles at this time increase by Δθ1 and Δθ2, respectively, compared to the comparative example.

  As described above, in the element 4 of the first embodiment, the belt engagement angle is larger than that of the element E of the comparative example, so that the contact area between the flank surfaces 4a and 4a that are the side surfaces of the element 4 and the pulleys 1 and 2 increases. . As a result, it is possible to prevent slippage in the rotational direction that occurs between the belt V and the pulleys 1 and 2, thereby achieving an improvement in frictional force.

  Then, by increasing the contact area between the element 4 and the pulleys 1 and 2 and improving the friction force (friction coefficient), if the belt pressing force is constant, the transmission is compared with the element E of the comparative example. The torque capacity can be increased and the belt torque transmission efficiency can be improved. Further, if the transmission torque capacity is constant, the belt pressing force can be reduced as compared with the element E of the comparative example, and the fuel consumption can be improved and the transmission can be downsized.

  The continuously variable transmission belt V has a large diameter and a small diameter when the gear ratio is other than 1: 1. At this time, both pulleys 1 and 2 have the same force for pulling the belt V left and right. The pulley pressing force received by the belt is larger in the large-diameter side pulley (the output pulley 2 for the low gear ratio and the input pulley 1 for the high gear ratio) having a larger belt engagement angle. For this reason, belt slip does not occur on the large diameter side, but belt slip occurs on the small diameter side.

  Here, since the centrifugal force due to the rotation of the pulleys 1 and 2 is relatively small on the small diameter side, the flow rate of the lubricating oil to the pulley outer diameter side due to the centrifugal force is small. As a result, even if the concave portion 41 and the convex portion 42 coincide with the centrifugal force direction as in the element 4 of the first embodiment, the frictional force does not increase significantly, and the friction torque does not easily increase.

[Characteristic effects in manufacturing methods]
12A and 12B are explanatory diagrams showing an element manufacturing method in a comparative example, in which FIG. 12A shows a material conveying process, FIG. 12B shows a material setting process, and FIG. 12C shows a punching process. FIG. 13 is an explanatory view showing an element manufactured in a comparative example, (a) shows an element perspective view, (b) shows an element flank portion, and (c) shows an arrow C in FIG. 8 (a). The sagging occurrence part by the punching seen from the direction is shown.

  As shown in FIG. 12, the element E of the comparative example is disposed at a position opposite to the punch 101 as a female die, a punch 102 as a male die, a plate presser 103 disposed at a position facing the die 101, and a punch 102. And a plate processing device 104 that is manufactured by a press working apparatus 100 that performs fine blanking processing that shears and punches the steel plate material W by relative movement of the die 101 and the punch 102.

  In the material conveying step, as shown in FIG. 12A, the steel plate material W is conveyed to the press working apparatus 100 from a direction perpendicular to the punching direction (shear direction) (horizontal direction).

  In the material setting process, as shown in FIG. 12B, the steel plate material W conveyed to the press working apparatus 100 is restrained by closing the die 101, the punch 102, the plate presser 103, and the plate receiver 104. At this time, hydraulic pressure is applied to the plate holder 103 and the plate holder 104, and a knife-edge V ring (not shown) formed on the plate holder 103 is driven into the steel plate material W.

  In the punching process, as shown in FIG. 12C, the contour of the element E is punched out from the steel plate material W constrained by the material setting process by fine blanking. At this time, the positions of the punch 102 and the plate holder 104 are fixed, and the die 101 and the plate presser 103 are lowered. As a result, the relative positions of the die 101 and the punch 102 are shifted to form a shear plane. In addition, a curved portion 106 called “sag” is generated on the shear cut surface of the steel sheet material W.

  When the element E is formed in the punching process, although not shown, the restraint of the plate-like element E by the die 101, the punch 102, the plate presser 103, and the plate receiver 104 is released, and the plate-like element E is discharged.

  Here, in the element E of the comparative example, the groove M formed in the flank surface 4a extends in the plate thickness direction of the element E. For this reason, when the steel sheet material W is punched into an element shape by fine blanking, the groove M is cut in the thickness direction at the same time as the punching (see FIG. 13B).

  Further, in the fine blanking process, the steel plate material W is always pressed flat by the die 101 and the plate retainer 103 during the processing to prevent bending deformation. However, as shown in FIG. It will occur. Since the element E of this comparative example is manufactured only by fine blanking, the curved portion (sag) 106 cannot be corrected and remains as it is. For this reason, the plate thickness in the vicinity of the cut surface is reduced as compared with the central portion of the element E.

  Thereby, the area where the flank surface 4a contacts the pulleys 1 and 2 decreases, and the surface pressure increases. As a result, the flank surface 4a and the sheave surfaces 11a, 12a, 21a, and 22a are likely to be worn, and there is a risk that problems due to this wear may occur early.

  On the other hand, the element 4 of Example 1 forms the recessed part 41 and the convex part 42 by pressing the groove processing tool 105 to the side surface of the punching element 4 ′ after the punching process as described above, and further flattening treatment. In the process, the swell 107 in the plate thickness direction accompanying the groove processing is flattened.

  Accordingly, the flank surface 4a is crushed, the curved portion (sag) 106 is corrected, and the area (element plate thickness) where the flank surface 4a contacts the pulleys 1 and 2 can be increased as compared with the comparative example. It is possible to prevent the occurrence of defects due to increase in wear and wear.

  Further, by forming the concave portion 41 and the convex portion 42 in the post-process of fine blanking as described above, the concave portion 41 and the convex portion 42 perpendicular to the punching direction can be formed.

Next, the effect will be described.
In the element of the belt type continuously variable transmission according to the first embodiment, the effects listed below can be obtained.

(1) Hang between the input pulley 1 with variable groove width in the input shaft direction, the output pulley 2 with variable groove width in the output shaft direction, and between the input pulley 1 and the output pulley 2 The belt V is a belt type belt in which a large number of plate-like elements 4 are stacked in the thickness direction and bundled by an endless band (laminated ring 3). In the step transmission, a concave portion 41 and a convex portion 42 are formed on the side surface (flank surface 4a) of the plate-like element 4 over the entire length from one end to the other end in a direction perpendicular to the plate thickness direction.
For this reason, by shortening the time required for oil film removal, an increase in the contact area between the side surface of the element and the pulley can be promoted, and an improvement in frictional force can be achieved.

(2) The concave portions 41 and the convex portions 42 have a plurality of rows of concave grooves and convex stripes formed alternately in the plate thickness direction.
For this reason, the effective flow path cross section for oil film removal can be expanded, and oil film removal can be performed more rapidly.

(3) In the element manufacturing method of a belt-type continuously variable transmission for manufacturing a plate-like element by fine blanking processing in which a steel plate material W is punched with high precision by controlling the flow of the material in the shearing portion, the plate-like element The concave portions 41 and the convex portions 42 formed on the four side surfaces (flank surface 4a) are formed in a subsequent process of the fine blanking process.
For this reason, the recessed part 41 and the convex part 42 of the orthogonal | vertical direction with respect to the punching direction can be formed.

(4) a die 101 that is a female die, a punch 102 that is a male die, a plate retainer 103 disposed at a position facing the die 101, and a plate receiver 104 disposed at a position facing the punch 102. And a material processing step of transporting the steel plate material W to the press working device 100, comprising a press working device 100 for performing a fine blanking process of shearing and punching the steel plate material W by relative movement of the die 101 and the punch 102. (FIG. 7 (a)) and the material setting step of constraining the steel sheet material W conveyed to the press working apparatus 100 by closing the die 101, the punch 102, the plate presser 103, and the plate support 104. (FIG. 7 (b)) and the steel plate material W restrained by the material setting step (FIG. 7 (b)), the contour of the element 4 is formed by the fine blanking process. The punching process (FIG. 7 (c)) and the punching element 4 ′ from the punching process (FIG. 7 (c)) are held by the punch 102 and the plate holder 104 to the groove processing position in the punching direction. The concave portion is formed by a coining process in which the groove moving tool 105 set in the plate retainer 103 is pressed and marked on both side portions of the relatively moved punching element 4 ′ and the element moving step (FIG. 7D) that moves relatively. 41 and the groove 42 forming the convex portion 42 (FIG. 7 (e)), and the coining process causes the plate-like element 4 to rise in the plate thickness direction 107 by the punch 102 and the plate receiver 104. A flattening process (FIG. 7 (f)) for flattening by pressing, and the plate-like elec- tric device by the die 101, the punch 102, the plate presser 103, and the plate support 104. The element discharging step (FIG. 7 (g)) for releasing the restraint of the ment 4 and discharging the plate-like element 4 that has completed the groove processing and the flattening processing is provided.
For this reason, the curved portion (sag) 106 is corrected by the fine blanking process by the groove processing and the flattening process, and the flank surface 4a is enlarged, thereby further increasing the frictional force.

Example 2 is an example in which the concave portions formed on the flank surface are formed as one row of concave grooves, and the convex portions are formed as two rows of convex stripes sandwiching the concave grooves.

First, the configuration will be described.
FIGS. 14A and 14B are diagrams showing the main part of the element of the belt-type continuously variable transmission according to the second embodiment. FIG. 14A is a side view of the element, and FIG. 14B is an enlarged view of the element flank portion.

  In the element 50 of the second embodiment, the concave portion 51 and the convex portion 52 are formed on the flank surface 5a which is a side surface in a direction perpendicular to the plate thickness direction. Here, the concave portions 51 are a row of concave grooves formed in the central portion in the plate thickness direction. Moreover, the convex part 52 is a 2 row | line | column convex line | wire formed in the both sides on both sides of the recessed part 51 which is a 1 line groove.

  By forming the concave portion 51 and the convex portion 52 in a direction perpendicular to the plate thickness direction of the element 50, the oil film removing ability by centrifugal force is improved, and the cross-sectional area of the concave portion 51 can be reduced. Thereby, in Example 2, the cross-sectional area of the convex part 52 is increased by arranging the concave parts 51 in one row, and the increase of the frictional force between the element 50 and the pulley sheave surface (not shown here) is further promoted. be able to.

  Furthermore, by arranging the recesses 51 in one row, it becomes easy to calculate the effective flow path sectional area for oil film removal, and the oil film removal time can be managed more accurately.

Next, the effect will be described.
In the element of the belt type continuously variable transmission according to the second embodiment, in addition to the effect (1) described above, the following effects can be obtained.

(5) The concave portions 51 are a single row of concave grooves formed in the central portion in the plate thickness direction, and the convex portions 52 are two rows of convex stripes formed on both sides of the single row of concave grooves. A certain configuration was adopted.
For this reason, the cross-sectional area of the recessed part 51 can be decreased, the cross-sectional area of the convex part 52 can be increased, and the increase in the frictional force (friction coefficient) between the element 50 and the pulley sheave surface can be further promoted.

  As mentioned above, although the element of the belt-type continuously variable transmission of this invention and its manufacturing method have been demonstrated based on Example 1 and Example 2, it is not restricted to these Examples about a concrete structure, Design changes and additions are allowed without departing from the spirit of the invention according to each claim of the claims.

  In the first embodiment, the groove processing step by coining and the flattening step for flattening the swell 107 are performed separately. For example, the punching element 4 ′ is sandwiched between the punch 102 and the plate receiver 104. Coining may be performed. In this case, the grooving process and the planarization process can be performed at the same time, and the number of man-hours can be reduced.

  Moreover, in Example 1, the example which set the recessed part and convex part formed in the flank surface of an element to the uneven | corrugated curved surface shape by a part of circular arc was shown. However, as an example of the shape of the concave portion and the convex portion, an uneven curved surface shape by a part of an ellipse may be set, or a flat portion may be left in the central portion of the unevenness, and curved surfaces may be set at both edge portions. Further, the concave portion may be V-shaped, or may be various other shapes in consideration of a semicircular arc shape or oil discharge performance.

  In the first embodiment, an example of an element constituting a belt applied to a belt-type continuously variable transmission of an engine vehicle is shown. However, the present invention is not limited to a belt-type continuously variable device mounted on another vehicle such as a hybrid or an electric vehicle. The present invention can also be applied to an element constituting a belt applied to a step transmission.

V Continuously Variable Transmission Belt 1 Input pulley 11 Fixed pulley 12 Slide pulley 11a, 12a Sheave surface 2 Output pulley 21 Fixed pulley 22 Slide pulley 21a, 22a Sheave surface 3 Laminated ring (endless band)
4 Element 4a Frank surface 4a1 One end (lower end) of the flank surface
4a2 The other end (upper end) of the flank surface
41 Concave part 42 Convex part

Claims (5)

An input pulley having a variable groove width in the input shaft direction, an output pulley having a variable groove width in the output shaft direction, and a belt that spans between the input pulley and the output pulley. The belt is a belt-type continuously variable transmission in which a large number of plate-like elements are stacked in the thickness direction and bundled by an endless band.
An element of a belt-type continuously variable transmission, wherein a concave portion and a convex portion are formed on the side surface of the plate-like element over the entire length from one end to the other end in a direction perpendicular to the plate thickness direction. In the element of the belt type continuously variable transmission according to claim 1,
The element of the belt-type continuously variable transmission is characterized in that the concave portion and the convex portion are a plurality of rows of concave grooves and ridges formed alternately in the plate thickness direction. In the element of the belt type continuously variable transmission according to claim 1,
The concave portion is a row of concave grooves formed at a central portion in the plate thickness direction, and the convex portion is two rows of convex stripes formed on both sides of the single row of concave grooves. Belt type continuously variable transmission element. In the element manufacturing method of a belt-type continuously variable transmission that manufactures a plate-like element by fine blanking processing in which a steel sheet material is precisely punched by controlling the flow of the material in the shearing part,
An element manufacturing method for a belt-type continuously variable transmission, characterized in that a concave portion and a convex portion formed on a side surface of the plate-like element are formed in a subsequent process of the fine blanking process. In the element manufacturing method of the belt type continuously variable transmission according to claim 4,
A die that is a female die, a punch that is a male die, a plate presser disposed at a position opposed to the die, and a plate receiver disposed at a position opposed to the punch, and the relative movement of the die and the punch Equipped with a press working device that performs a fine blanking process by shearing and punching the steel sheet material,
A material conveying step of conveying the steel sheet material to the pressing device;
A material setting step of constraining the steel plate material conveyed to the press working device by closing the die, the punch, the plate presser, and the plate receiver,
From the steel sheet material constrained by the material setting process, a punching process for punching the outline of the element by the fine blanking process,
An element moving step of relatively moving the punching element from the punching step to the groove processing position in the punching direction while being sandwiched between the punch and the plate holder;
A groove processing step of forming the concave portion and the convex portion by coining processing for pressing and marking the groove processing tool set to the plate press on both side portions of the punching element moved relative to each other;
A flattening treatment step of flattening the plate-shaped element in the plate thickness direction by the coining by narrowing the pressure with the punch and the plate receiver;
An element discharging step of releasing the plate-like element after releasing the restraint of the plate-like element by the die, the punch, the plate presser and the plate holder, and completing the groove processing and the flattening process;
A method of manufacturing an element of a belt-type continuously variable transmission, comprising:

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