JP2019168100A - Element for transmission belt and transmission belt - Google Patents

Abstract

To further improve the durability of an element for a transmission belt with respect to rolling.SOLUTION: An element of a transmission belt wound to a pulley of a continuously variable transmission includes: a pair of first side faces which are inclined so as to separate from each other as progressing toward an external peripheral side from an internal peripheral side of the transmission belt in a radial direction; a pair of second side faces located at the external peripheral side in the radial direction rather than the first side faces; a connecting part for connecting the first side faces and the second side faces; and a locking edge part including a contact line of both the elements being a pivot of a turn of the adjacent elements. Inclination angles of the first side faces with respect to the radial direction are larger than inclination angles of the second side faces with respect to the radial direction, and the connecting part is located between the thinnest part of a pillar part and the locking edge part in the radial direction.SELECTED DRAWING: Figure 3

Description

  The present disclosure includes a barrel portion having a saddle surface that contacts a ring of a transmission belt wound around a pulley of a continuously variable transmission, and a pair of arms extending from the barrel portion so as to be located on both sides in the width direction of the saddle surface. And a transmission belt including the same.

  Conventionally, as a power transmission belt element, a body portion (body portion) extending left and right, a pair of pillar portions extending upward from the left and right ends of the upper portion of the body portion, and a locking edge formed on the front main surface and extending left and right A device having a portion is known (for example, see Patent Document 1). The pair of side surfaces of the element extends in the radial direction on the outer peripheral side of the V surface, and a pair of V surfaces that are inclined so as to be separated from each other toward the outer peripheral side from the inner peripheral side in the radial direction of the transmission belt. And a flat surface formed in the pillar portion.

JP 2006-153089 A

  Here, when the torque is transmitted by the transmission belt of the continuously variable transmission, the element is a chord portion of the transmission belt that travels from the secondary pulley toward the primary pulley, and the shaft of the shaft through which the element passes through the center of the trunk portion. A phenomenon called rolling that swings around may occur. Then, when the element is in contact with the primary pulley (sheave) in a rolling state, a large stress is generated on the outer peripheral side portion of the pillar portion, which may reduce the durability of the element and the transmission belt. However, in the said patent document 1, durability of the element with respect to the said rolling is not considered at all. Further, during the operation of the continuously variable transmission, the element swings in the front-rear direction in the traveling direction of the transmission belt. If the swinging (pitching) of the transmission belt increases, the durability of the element and the transmission belt decreases. There is a risk that.

  Accordingly, the main object of the present disclosure is to further improve the durability of the power transmission belt element.

  An element for a transmission belt according to the present disclosure includes a body having a saddle surface that contacts a ring of a transmission belt wound around a V-shaped groove of a pair of pulleys of a continuously variable transmission, and both sides in the width direction of the saddle surface. In the transmission belt element including a pair of pillar portions extending from the body portion so as to be positioned, a pair of the belts inclined so as to be separated from each other toward the outer peripheral side in the radial direction of the transmission belt. A first side surface, a pair of second side surfaces located on the outer peripheral side in the radial direction with respect to the first side surface, a connecting portion connecting the first side surface and the second side surface, and formed on the front surface or the back surface; A rocking edge portion including a contact line between both of the adjacent transmission belt elements as a fulcrum of rotation, and the pillar portion has a change in length in the width direction in the radial direction. And the smallest detail in which the length in the width direction is the shortest is located on the outer peripheral side with respect to the saddle surface, and the inclination angle of the first side surface with respect to the radial direction is the first angle with respect to the radial direction. It is larger than the inclination angle of two side surfaces, and the connecting portion is located between the most detailed portion and the rocking edge portion in the radial direction.

  In the transmission belt element of the present disclosure, the connecting portion that connects the first side surface and the second side surface located on the outer peripheral side in the radial direction of the transmission belt with respect to the first side surface is the most detailed pillar portion and the locking edge portion. Located in the radial direction. As a result, the stress generated near the finest part of the pillar portion when the transmission belt element is in contact with the pulley in a rolling state is reduced, and the resistance force due to the friction generated between the transmission belt element and the pulley ( The moment) can satisfactorily suppress the pitching of the transmission belt element. As a result, the durability of the transmission belt element can be further improved.

It is a schematic block diagram which shows an example of the continuously variable transmission which has a transmission belt containing the element for transmission belts of this indication. It is a schematic block diagram which shows the element for transmission belts of this indication. It is an enlarged view which shows the element for power transmission belts of this indication. It is a graph which shows the analysis result of the relationship between the distance from the center in the width direction of an element to a connecting surface, and the stress which generate | occur | produces in a pillar part resulting from the rolling of an element.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram illustrating a continuously variable transmission (CVT) 1 of the present disclosure. A continuously variable transmission 1 shown in FIG. 1 is mounted on a vehicle, and includes a primary shaft (first shaft) 2 as a drive side rotating shaft, and a primary pulley (first pulley) provided on the primary shaft 2. ) 3, a secondary shaft (second shaft) 4 as a driven side rotating shaft arranged in parallel with the primary shaft 2, a secondary pulley (second pulley) 5 provided on the secondary shaft 4, and a transmission belt 10 Including. As illustrated, the transmission belt 10 is wound around a pulley groove (V-shaped groove) of the primary pulley 3 and a pulley groove (V-shaped groove) of the secondary pulley 5.

  The primary shaft 2 is connected to an input shaft (not shown) connected to a power generation source such as a vehicle engine (internal combustion engine) via a forward / reverse switching mechanism (not shown). The primary pulley 3 includes a fixed sheave 3a formed integrally with the primary shaft 2, and a movable sheave 3b supported slidably in the axial direction by the primary shaft 2 via a ball spline or the like. The secondary pulley 5 is supported by the secondary shaft 4 so as to be slidable in the axial direction through a fixed sheave 5a formed integrally with the secondary shaft 4 and a ball spline, and is attached in the axial direction by a return spring 8. And a movable sheave 5b.

  Further, the continuously variable transmission 1 includes a primary cylinder 6 that is a hydraulic actuator for changing the groove width of the primary pulley 3, and a secondary cylinder 7 that is a hydraulic actuator for changing the groove width of the secondary pulley 5. including. The primary cylinder 6 is formed behind the movable sheave 3 b of the primary pulley 3, and the secondary cylinder 7 is formed behind the movable sheave 5 b of the secondary pulley 5. Hydraulic fluid is supplied to the primary cylinder 6 and the secondary cylinder 7 from a hydraulic control device (not shown) so as to change the groove width between the primary pulley 3 and the secondary pulley 5. The secondary shaft 4 is connected to drive wheels (not shown) of the vehicle via a gear mechanism, a differential gear, and a drive shaft.

  In the present embodiment, a stepped portion is formed at the end of the primary shaft 2 opposite to the engine (the left end in FIG. 1). And between the said step part and the primary piston 60 of the primary cylinder 6, it can contact | abut with the edge part (left edge part in FIG. 1) on the opposite side to the engine side of the movable sheave 3b of the primary pulley 3. Thus, an annular end plate 65 is interposed. Further, the primary shaft 2 is formed with a stopper portion 2s so as to be able to come into contact with the end portion on the fixed sheave 3a side of the spline teeth 3s formed on the inner peripheral surface of the movable sheave 3b.

  When the movable sheave 3b of the primary pulley 3 is separated from the fixed sheave 3a and contacts the end plate 65, the movement of the movable sheave 3b with respect to the primary shaft 2 in the direction away from the fixed sheave 3a is restricted. Thereby, the width of the pulley groove of the primary pulley 3 is maximized, and accordingly, the width of the pulley groove of the secondary pulley 5 is set to the minimum, so that the speed ratio γ of the continuously variable transmission 1 is maximized. Further, when the spline teeth 3 s formed on the inner peripheral surface of the movable sheave 3 b abuts on the stopper portion 2 s formed on the primary shaft 2, the movable sheave 3 b moves relative to the primary shaft 2 in a direction approaching the fixed sheave 3 a. Is regulated. As a result, the width of the pulley groove of the primary pulley 3 is minimized, and accordingly, the width of the pulley groove of the secondary pulley 5 is set to the maximum by the transmission belt 10, whereby the transmission ratio γ of the continuously variable transmission 1 is increased. Be minimized. The continuously variable transmission 1 is configured such that the primary shaft 2 and the secondary shaft 4 are selectively connected to the input shaft, and the primary shaft 2 and the secondary shaft 4 are selectively connected to the drive shaft of the vehicle. May be.

  FIG. 2 is a schematic configuration diagram showing the transmission belt 10. As shown in the figure, the transmission belt 10 is formed by laminating a plurality of (for example, nine in this embodiment) ring members 11 that are elastically deformable in the thickness direction (ring radial direction). The laminated ring 12, one retainer ring 15, and a plurality (for example, several hundreds) of elements 20 arranged in an annular shape (bundled) along the inner peripheral surface of the laminated ring 12 are included. In the present embodiment, the element 20 includes a first element and a second element having a thickness (maximum thickness) slightly larger (for example, about 0.1 mm) than the first element. A plurality of the second elements are arranged adjacent to each other. Thereby, when torque is transmitted between the primary pulley 3 and the secondary pulley 5 by the transmission belt 10, it is possible to suppress generation of vibration and noise. Since the structures other than the thicknesses of the first and second elements are common, both are hereinafter collectively referred to as “element 20”.

  The plurality of ring members 11 constituting the laminated ring 12 are each elastically deformable cut out from a steel plate drum, and are processed to have substantially the same thickness and different perimeters predetermined for each. Has been. The retainer ring 15 is an elastically deformable material cut out from, for example, a steel plate drum, and has a thickness substantially equal to or thinner than that of the ring material 11. In addition, the retainer ring 15 has an inner peripheral length that is longer than the outer peripheral length of the outermost ring material 11 o of the laminated ring 12. Thereby, in a state where the laminated ring 12 and the retainer ring 15 are arranged concentrically (no load state where no tension acts), as shown in FIG. 2, the outer peripheral surface of the outermost ring material 11o and the retainer ring 15 An annular clearance is formed between the inner peripheral surface.

  Each element 20 has a symmetrical outer shape (planar shape) punched from a steel plate by, for example, pressing, and as shown in FIG. 2, a body portion 21 extending horizontally in the figure, A pair of pillar portions 22 extending in the same direction from both ends, and a single ring housing portion (concave portion) defined between the pair of pillar portions 22 so as to open to the free end side of each pillar portion 22 ) 23 and a pair of side surfaces 20s formed so as to be spaced apart from the inner peripheral side to the outer peripheral side of the transmission belt 10 (laminated ring 12).

  In the present embodiment, the edge portion 21ei of the body portion 21 on the inner peripheral side of the transmission belt 10 is formed flat as shown in FIG. The pair of pillar portions 22 extends from both sides in the width direction of the saddle surface 23s, which is the bottom surface of the ring housing portion 23, to the outer peripheral side (the direction from the inner peripheral side to the outer peripheral side of the transmission belt 10, that is, upward in the drawing). The length (width) in the width direction of the saddle surface 23 s is changed in the radial direction of the transmission belt 10. Further, a hook portion 22f protruding in the width direction of the saddle surface 23s is formed at the free end portion of each pillar portion 22. The pair of hook portions 22 f are opposed to each other with an interval slightly longer than the width of the laminated ring 12 (ring material 11) and shorter than the width of the retainer ring 15. Further, as shown in FIG. 3, each pillar portion 22 of the element 20 has a flat inner surface 22i that is inclined so as to be separated from the saddle surface 23s in the width direction as it goes from the trunk portion 21 side to the hook portion 22f side. A concave curved surface (for example, a concave cylindrical surface) Ri that smoothly continues to the inner surface 22i and the saddle surface 23s and a concave curved surface Ro (for example, a concave cylindrical surface) that smoothly continues to the inner surface 22i and the inner peripheral surface 22fi of the hook portion 22f. Surface).

  As shown in FIG. 2, the laminated ring 12 is disposed in the ring accommodating portion 23, and the saddle surface 23s of the ring accommodating portion 23 is in contact with the laminated ring 12, that is, the inner peripheral surface of the innermost layer ring material 11i. The saddle surface 23s has a left-right symmetrical convex curved surface shape (crowning shape) that gradually slopes downward in the figure as it goes outward in the width direction with the central portion in the width direction as a top portion T. Accordingly, it is possible to center the laminated ring 12 by applying a centripetal force toward the top T to the laminated ring 12 by friction with the saddle surface 23s. However, the saddle surface 23 s may include a plurality of convex curved surfaces that are curved toward the outer peripheral side in the radial direction of the transmission belt 10.

  Further, the elastically deformed retainer ring 15 is fitted into the ring accommodating portion 23 from between a pair of hook portions 22 f of each element 20. The retainer ring 15 is disposed between the outer peripheral surface of the outermost layer ring material 11o of the laminated ring 12 and the hook portion 22f of each element 20, surrounds the laminated ring 12, and together with the pair of pillar portions 22, each element 20 Is prevented from dropping from the laminated ring 12 or from the element 20. Thereby, the plurality of elements 20 are bound (arranged) in an annular shape along the inner peripheral surface of the laminated ring 12. In the present embodiment, the retainer ring 15 is formed with a single or a plurality of openings (elongate holes) (not shown), whereby the retainer ring 15 can be easily elastically deformed and the assembling property to the element 20 is ensured. can do.

  A clearance is formed between the outer peripheral surface of the outermost ring material 11o of the laminated ring 12 and the inner peripheral surface of the retainer ring 15 as described above, and basically the retainer ring 15 is in operation during the operation of the continuously variable transmission 1. There is no tension, etc. Thereby, in the element 20, it is not necessary to enlarge the pillar part 22 and the hook part 22f in order to ensure rigidity and the like, and the element 20 is laminated on both sides of the head part extending from the center part in the width direction of the trunk part to the outer peripheral side. Compared to a general element in which a ring is disposed, the area of the portion of the pillar portion 22 that protrudes to the outer peripheral side from the laminated ring 12 can be reduced. Therefore, it is possible to reduce the cost of the transmission belt 10 and thus the continuously variable transmission 1 by reducing the material cost of the element 20.

  Further, as shown in FIG. 3, each side surface 20 s of the element 20 is formed in the body portion 21 and the pillar portion 22 so as to extend from the inner peripheral side edge portion 21 ei side of the body portion 21 to the outer peripheral side. A first side surface 20sa, a second side surface 20sb formed on the pillar portion 22 so as to be positioned on the outer peripheral side in the radial direction of the transmission belt 10 (see the alternate long and short dash line in FIG. 2) relative to the first side surface 20sa; A convex surface (for example, a cylindrical surface) connecting surface (connecting portion) 20sc formed on the pillar portion 22 so as to be smoothly connected to the two side surfaces 20sa and 20sb.

  The pair of first side surfaces 20sa is inclined so as to be separated from the inner peripheral side in the radial direction of the transmission belt 10 toward the outer peripheral side, and the angles formed by the pair of first side surfaces 20sa are the primary pulley 3 and the secondary pulley. 5 is set to be approximately equal to the opening angle of the pulley groove 5 (in this embodiment, slightly larger than the design value of the opening angle). As a result, the first side surface 20sa of the element 20 is brought into frictional contact with the surfaces of the pulley grooves of the primary pulley 3 and the secondary pulley 5 to receive the clamping pressure from the pulleys 3 and 5, and the primary pulley 3 to the secondary pulley 5 are caused by the frictional force. It becomes a flank surface (torque transmission surface) that transmits torque to the heel. In the present embodiment, the surface of each first side surface 20sa has irregularities (not shown) for holding hydraulic oil for lubricating and cooling the contact portions between the element 20 and the primary pulley 3 and the secondary pulley 5 (a plurality of grooves). ) Is formed.

  The pair of second side surfaces 20sb extends in the radial direction of the transmission belt 10 in parallel with each other. That is, the inclination angle (absolute value, 0 ° in this embodiment) of the second side surface 20sb with respect to the radial direction of the transmission belt 10 is smaller than the inclination angle (absolute value) of the first side surface 20sa with respect to the radial direction. Thereby, when the element 20 is clamped by the primary pulley 3 or the secondary pulley 5, the pair of second side surfaces 20sb basically does not contact the surface of the pulley groove.

  Further, as shown in FIGS. 2 and 3, the front surface (one surface) of the element 20 is formed in a pair of convex curved rocking edge portions (contact regions) 25, a non-contact portion 27, and a body portion 21. And 21s with a tapered surface (slope).

  Each rocking edge portion 25 is a short belt-like convex curved surface. In this embodiment, the rocking edge portion 25 is a cylindrical surface or an elliptical cylindrical surface (curved surface) having a predetermined radius of curvature and having a radial width. Each rocking edge portion 25 includes a contact line that makes adjacent elements 20 contact each other and serves as a fulcrum for their rotation, and the position of the contact line depends on the speed ratio γ of the continuously variable transmission 1. And fluctuate within the range of the locking edge portion 25. In the present embodiment, the end 25o of the rocking edge portion 25 on the outer peripheral side of the transmission belt 10 (the upper side in the drawing, ie, the pillar portion 22 side) is the outer peripheral side in the radial direction of the transmission belt 10 from the saddle surface 23s (top portion T). The end 25i of the rocking edge portion 25 on the inner peripheral side of the transmission belt 10 (the lower side in the drawing, that is, the tapered surface 21s side) is the inner periphery in the radial direction of the transmission belt 10 from the saddle surface 23s (bottom portion). Located on the side. In the present embodiment, the pair of locking edge portions 25 are formed on the front surface of the element 20 at intervals in the width direction of the saddle surface 23 s so as to straddle the corresponding pillar portions 22 and trunk portions 21. The However, the locking edge portion 25 may be formed so as to be included only in one of the pillar portion 22 and the trunk portion 21. Further, the locking edge portion 25 may be formed on the back surface of the element 20.

  The non-contact portion 27 is a band-shaped recess formed in the body portion 21 so as to open in the saddle surface 23s and extend in the width direction along the saddle surface 23s. Both are divided in the said width direction. In the present embodiment, the end portion 27i (see FIGS. 2 and 3) on the inner peripheral side of the non-contact portion 27 is on the inner peripheral side (lower side in the drawing) than the end portion 25i on the inner peripheral side of the locking edge portion 25. Located in. Further, in the present embodiment, the non-contact portion 27 is formed such that the depth at both ends in the width direction gradually decreases as the locking edge portion 25 approaches, and the portion between both ends has a substantially constant depth. Has been. The width of the non-contact portion 27 having a substantially constant depth is narrower than the width of the laminated ring 12. Thereby, it is possible to suppress the stress concentration in the vicinity of both end portions in the width direction of the non-contact portion 27 and further improve the durability of the element 20.

   By forming such a non-contact portion 27 in each element 20, in the transmission belt 10, contact with the adjacent element 20 other than the rocking edge portion 25, that is, contact between the adjacent element 20 and the non-contact portion 27. Can be suppressed satisfactorily. As a result, it is possible to prevent the element 20 from being deformed by applying a load from the central portion in the width direction of the element 20 on which a large moment acts to the adjacent element 20, and to further improve the durability of each element 20. Is possible.

  The tapered surface 21s is formed so as to be continuous with the rocking edge portion 25 and to approach the back surface of the element 20 from the rocking edge portion toward the inner peripheral edge 21ei (lower side in the figure) of the trunk portion 21. It is a flat slope. Further, the taper surface 21s is formed with one projection (dimple) 21p so as to be positioned at the center in the width direction of the front surface of the body portion 21, and on the back surface of the element 20 (body portion 21), A recess 21r is formed so as to be positioned on the back side of the protrusion 21p. When the transmission belt 10 is assembled, the protrusion 21p of the adjacent element 20 is loosely fitted into the recess 21r. Thus, by forming the protrusion 21p and the recess 21r on the body portion 21 of the element 20, the element 20 can be further reduced in height.

  Furthermore, in this embodiment, the front surface (mainly the front surface of the pillar portion 22) of the element 20 on the outer peripheral side (the upper side in FIG. 2) of the locking edge portion 25 and the back surface (the other surface) of the element 20 are as shown in FIG. As shown in FIG. 4, they are flat and parallel to each other. Thereby, the pillar portion 22 of the element 20 has a substantially constant thickness te. Further, since the non-contact portion 27 is recessed on the back side from the surface of the rocking edge portion 25, the thickness of the saddle surface 23 s is smaller than the thickness te of the pillar portion 22. The inclination angle of the tapered surface 21s is set in consideration of the thickness te of the pillar portion 22 so that the tapered surface 21s does not contact the back surface of the adjacent element 20. A flat part extending in parallel with the back surface of the element 20 may be formed around the protrusion 21p.

  When torque is transmitted from the primary pulley 3 to the secondary pulley 5 by the transmission belt 10 including the plurality of elements 20 as described above, the two string portions that are not wound around the pulleys 3 and 5 of the transmission belt 10 Among them, a phenomenon called rolling in which the element 20 swings around an axis passing through the center of the trunk portion 21, that is, the protrusion 21 p, occurs particularly in the chord portion where the element 20 advances from the secondary pulley 5 toward the primary pulley 3. Sometimes. For this reason, when the element 20 comes into contact with the primary pulley 3 (the fixed sheave 3a and the movable sheave 3b) in a rolled state, a large stress is generated in the pillar portion 22, thereby the durability of each element 20 and the transmission belt 10 is increased. May decrease.

  Based on this, the present inventors basically have a first side surface 20sa serving as a flank surface to reduce the stress generated in the pillar portion 22 when the element 20 is in contact with the primary pulley 3 in a rolled state, Paying attention to the position of the connecting surface 20sc that connects the second side surface 20sb not contacting the surface of the pulley groove to the pillar portion due to the distance from the center in the width direction of the element 20 to the connecting surface 20sc and the rolling of the element 20 The relationship with the stress generated at 22 was examined.

Specifically, a plurality of distances L (see FIG. 3) from the center in the width direction of the element 20 to the intersection (intersection line) between the extended surface of the first side surface 20sa and the extended surface of the second side surface 20sb are changed. When a predetermined load (for example, about 50 N) is applied to the intersecting portion in a state where the center portion in the width direction of each model is completely constrained, a concave surface inside the pillar portion 22 is prepared. The minimum principal stress (compressive stress) σ _min generated was obtained by analysis. Note that the connecting surface 20sc (the intersection of the extended surface of the first side surface 20sa and the extended surface of the second side surface 20sb moves to the outer peripheral side of the transmission belt 10 as the distance L is longer, and the transmission distance is shorter as the distance L is shorter. It moves to the inner peripheral side of the belt 10.

FIG. 4 shows an analysis result of the relationship between the distance L and the minimum principal stress σ _min generated at the pillar portion 22. As shown in the figure, the absolute value of the minimum principal stress σ _min decreases as the distance L decreases. Further, according to the analysis performed separately, the intersection (intersection line) between the extended surface of the first side surface 20sa and the extended surface of the second side surface 20sb is the width of the pillar portion 22 (the saddle surface 23s of the saddle surface 23s) in the radial direction of the transmission belt 10. If each element is located on the inner side of the smallest detail 22n (refer to FIG. 3) in which the width in the width direction is the smallest and on the outer peripheral side of the outer peripheral end 25o of the locking edge 25, each element Pitching of the element 20 can be satisfactorily suppressed by a resistance force (moment) caused by friction generated between the pulley 20 and the primary pulley 3 and the like, thereby reducing the efficiency, durability, noise, and torque capacity due to the pitching. It has also been found that local wear of the first side surface 20sa contacting the pulley groove can be reduced while suppressing.

  From this analysis result, in the transmission belt 10 of the present embodiment, the connecting surface 20sc between the first side surface 20sa and the second side surface 20sb is the most detailed 22n of the pillar portion 22 and the outer end 25o of the locking edge portion 25. The pillar portion 22 is formed so as to be located in the radial direction between the pillar portions 22. As a result, it is possible to sufficiently reduce the stress generated in the vicinity of the most detailed portion 22n of the pillar portion 22 when the element 20 comes into contact with the primary pulley 3 in a rolled state. Further, the center of gravity of the contact surface between the element 20 and the sheaves 3a, 3b, etc. is brought close to the rocking edge 25, that is, the contact line, and the resistance force (moment) due to friction generated between the element 20 and the primary pulley 3 or the like Pitting of the transmission belt element can be satisfactorily suppressed. As a result, the durability of the element 20 can be further improved. Further, as can be seen from FIG. 4, the radial direction between the boundary B between the concave curved surface Ro continuing to the inner peripheral surface 22fi of the hook portion 22f and the inner surface 22i of the pillar portion 22 and the end portion 25o on the outer peripheral side of the rocking edge portion 25. By forming the connecting surface 20sc in the pillar portion 22 so as to be positioned between the two, the stress generated in the vicinity of the most detailed portion 22n of the pillar portion 22 when the element 20 contacts the primary pulley 3 in a rolled state is further increased. Can be reduced.

  Further, by forming the pair of second side surfaces 20 sb in the pillar portion 22 so as to extend in parallel and in the radial direction, the primary pulley 3 and the second pulley 20 are wound when the element 20 is wound around the primary pulley 3 in a rolled state. It is possible to suppress the two side surfaces 20sb from strongly hitting, and to further improve the durability of the element 20 against rolling. However, if the angle between the pair of second side surfaces 20sb is smaller than the angle formed between the pair of first side surfaces 20sa, the pair of second side surfaces 20sb is the inner side in the radial direction of the transmission belt 10. You may form so that it may mutually space apart as it goes to an outer peripheral side from the circumferential side.

  As described above, the transmission belt element of the present disclosure has the ring (12) of the transmission belt (10) wound around the V-shaped groove of the pair of pulleys (3, 5) of the continuously variable transmission (1). A barrel portion (21) having a saddle surface (23s) in contact with a pair of pillar portions (22) extending from the barrel portion (21) so as to be located on both sides in the width direction of the saddle surface (23s) ) Including a pair of first side surfaces (20sa) inclined so as to be separated from each other toward the outer peripheral side from the inner peripheral side in the radial direction of the transmission belt (10), A pair of second side surfaces (20sb) located on the outer peripheral side in the radial direction from the first side surface (20sa), and a connecting portion (20sc) that connects the first side surface (20sa) and the second side surface (20sb). When, A rocking edge portion (25) formed on a surface or a back surface and including a contact line between both of the adjacent transmission belt elements (20) serving as a fulcrum of rotation, and the pillar portion (22) The most detailed portion (22n) in which the length in the width direction changes in the radial direction and the length in the width direction is the shortest is formed so as to be located on the outer peripheral side with respect to the saddle surface (23s), and the diameter An inclination angle of the first side surface (20sa) with respect to the direction is larger than an inclination angle of the second side surface (20sb) with respect to the radial direction, and the connecting portion (20sc) has the most detailed (22n) and the rocking edge. It is located in the said radial direction with a part (25).

  In the transmission belt element of the present disclosure, the connecting portion that connects the first side surface and the second side surface located on the outer peripheral side in the radial direction of the transmission belt with respect to the first side surface is the most detailed pillar portion and the locking edge portion. Located in the radial direction. As a result, the stress generated near the finest part of the pillar portion when the transmission belt element is in contact with the pulley in a rolling state is reduced, and the resistance force due to the friction generated between the transmission belt element and the pulley ( The moment) can satisfactorily suppress the pitching of the transmission belt element. As a result, the durability of the transmission belt element can be further improved.

  Further, the pillar portion (22) includes a hook portion (22f) protruding from the free end portion toward the saddle surface (23s) side, and the head portion (21) side toward the hook portion (22f) side as described above. A concave curved surface (22i) inclined so as to be separated from the saddle surface (23s) in the width direction, and a concave curved surface (22fi) smoothly continuous with the inner surface (22i) and the inner peripheral surface (22fi) of the hook portion (22f). Ro), and the connecting surface (20sc) is between the boundary (B) between the concave curved surface (Ro) and the inner surface (22i) and the rocking edge portion (25) in the radial direction. May be located. As a result, it is possible to further reduce the stress generated in the vicinity of the finest part of the pillar portion when the transmission belt element is in contact with the pulley in a rolled state.

  Further, a projection (21p) is formed on one surface of the body (21), and the projection (21p) formed on the adjacent transmission belt element (20) is fitted on the other surface. A recessed portion (21r) that fits in may be formed. Accordingly, it is possible to further reduce the height of the transmission belt element while improving durability against rolling of the transmission belt element.

  The angle between the pair of first side surfaces (20sa) may be substantially equal to the opening angle of the V-shaped groove, and the pair of second side surfaces (20sb) are parallel to each other and in the radial direction. It may extend. As a result, when the transmission belt element is wound around the pulley in a rolled state, the pulley and the second side surface are prevented from strongly hitting, and the durability of the transmission belt element against rolling can be further improved. It becomes possible.

  Furthermore, the end (25i) on the inner peripheral side of the locking edge portion (25) may be located on the inner peripheral side with respect to the saddle surface (23s), and the end of the locking edge portion (25) The outer peripheral end (25o) may be located closer to the outer peripheral side than the saddle surface (23s).

  The transmission belt according to the present disclosure includes a pair of pillars extending from the body portion (21) so as to be positioned on both sides in the width direction of the saddle surface (23s) and the body portion (21) having a saddle surface (23s). A plurality of elements (20) having a portion (22) and a ring (12) disposed between the pair of pillar portions (22) of the plurality of elements (20) so as to contact the saddle surface (23s) In the transmission belt (10) wound around the V-shaped groove of the pair of pulleys (3, 5) of the continuously variable transmission (1), each of the elements (20) is connected to the transmission belt (10 ) In the radial direction, a pair of first side surfaces (20sa) that are inclined so as to be separated from each other toward the outer peripheral side, and a pair that is positioned on the outer peripheral side in the radial direction with respect to the first side surface (20sa). A second side surface (20sb), a connecting portion (20sc) connecting the first side surface (20sa) and the second side surface (20sb), and a rotation between adjacent elements (20) formed on the front surface or the back surface. And a rocking edge portion (25) including both contact lines serving as a fulcrum of movement, and the pillar portion (22) has a length in the width direction that varies in the radial direction and a length in the width direction. The shortest detail (22n) is formed so as to be located on the outer peripheral side with respect to the saddle surface (23s), and the inclination angle of the first side surface (20sa) with respect to the radial direction is the first angle with respect to the radial direction. The connecting portion (20sc) is larger than the inclination angle of two side surfaces (20sb), and is located between the most detailed portion (22n) and the rocking edge portion (25) in the radial direction. It is.

  In the element of the transmission belt of the present disclosure, the connecting surface between the first side surface and the second side surface located on the outer peripheral side in the radial direction of the transmission belt with respect to the first side surface is the most detailed of the pillar portion and the locking edge portion. Located in the radial direction. As a result, when the element is in contact with the pulley in a rolling state, the stress generated in the vicinity of the finest part of the pillar portion is reduced, and the resistance force (moment) generated by friction between the element and the pulley is used to reduce the stress of the element. Pitting can be suppressed satisfactorily. As a result, the durability of the element can be further improved.

  And the invention of this indication is not limited to the above-mentioned embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the above-described embodiment is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column.

  The invention of the present disclosure can be used in the manufacturing industry of continuously variable transmissions and transmission belts.

  1 continuously variable transmission, 2 primary shaft, 2s stopper, 3 primary pulley, 3a, 5a fixed sheave, 3b, 5b movable sheave, 3s spline teeth, 4 secondary shaft, 5 secondary pulley, 6 primary cylinder, 60 primary piston, 65 End plate, 7 Secondary cylinder, 8 Return spring, 10 Transmission belt, 11 Ring material, 11i Innermost layer ring material, 11o Outermost layer ring material, 12 Laminated ring, 15 Retainer ring, 20 Element, 20s Side surface, 20sa First side surface , 20sb second side, 20sc connecting surface, 21 trunk, 21ei edge, 21p protrusion, 21r recess, 21s tapered surface, 22 pillar portion, 22f hook portion, 22i inner surface, 23 ring housing portion, 23s saddle surface, 2 Rocking edge portion, 25i, 25o, 27i end, 27 non-contact portion, Ri, Ro concave surface, T top.

Claims (6)

A body portion having a saddle surface that contacts a ring of a transmission belt wound around a V-shaped groove of a pair of pulleys of the continuously variable transmission, and extends from the body portion so as to be positioned on both sides in the width direction of the saddle surface. In the element for a transmission belt including a pair of the pillar portions that are taken out,
A pair of first side surfaces that incline so as to be spaced apart from the inner peripheral side to the outer peripheral side in the radial direction of the transmission belt;
A pair of second side surfaces located on the outer peripheral side in the radial direction from the first side surface;
A connecting portion connecting the first side surface and the second side surface;
A rocking edge portion formed on the front surface or the back surface and including a contact line between both of the adjacent transmission belt elements serving as a fulcrum of rotation;
The pillar portion is formed so that the length in the width direction changes in the radial direction and the smallest detail in which the length in the width direction is the shortest is located on the outer peripheral side from the saddle surface,
An inclination angle of the first side surface with respect to the radial direction is larger than an inclination angle of the second side surface with respect to the radial direction, and the connecting portion is positioned between the most detailed portion and the rocking edge portion in the radial direction. Element for transmission belt. In the element for power transmission belts according to claim 1,
The pillar portion includes a hook portion that protrudes from the free end portion toward the saddle surface, an inner surface that is inclined so as to be spaced apart from the saddle surface in the width direction from the trunk portion side toward the hook portion side, and A concave curved surface that smoothly continues to the inner surface and the inner peripheral surface of the hook portion,
The connecting surface is an element for a transmission belt positioned between the boundary between the concave curved surface and the inner surface and the rocking edge portion in the radial direction. The power transmission belt element according to claim 1 or 2,
A transmission belt element in which a protrusion is formed on one surface of the body portion and a recess into which the protrusion formed on the adjacent transmission belt element is fitted is formed on the other surface. In the element for power transmission belts as described in any one of Claim 1 to 3,
The angle between the pair of first side surfaces is substantially equal to the opening angle of the V-shaped groove, and the pair of second side surfaces are parallel to each other and extend in the radial direction. In the element for power transmission belts as described in any one of Claim 1 to 4,
An end on the inner peripheral side of the rocking edge portion is positioned on the inner peripheral side with respect to the saddle surface, and an end on the outer peripheral side of the locking edge portion is positioned on the outer peripheral side with respect to the saddle surface. Element for transmission belt. A plurality of elements having a body portion having a saddle surface and a pair of pillar portions extending from the body portion so as to be located on both sides in the width direction of the saddle surface, and the plurality of elements so as to contact the saddle surface A transmission belt including a ring disposed between the pair of pillar portions of the element and wound around the V-shaped grooves of the pair of pulleys of the continuously variable transmission,
Each of the elements is
A pair of first side surfaces that incline so as to be spaced apart from the inner peripheral side to the outer peripheral side in the radial direction of the transmission belt;
A pair of second side surfaces located on the outer peripheral side in the radial direction from the first side surface;
A connecting portion connecting surface connecting the first side surface and the second side surface;
Including a rocking edge portion formed on the front surface or the back surface and including a contact line between both of the adjacent elements serving as a fulcrum of rotation,
The pillar portion is formed such that a length in the radial direction changes in the radial direction and the smallest detail in which the length in the width direction is the shortest is located on the outer peripheral side with respect to the saddle surface. An inclination angle of the first side surface with respect to the direction is larger than an inclination angle of the second side surface with respect to the radial direction, and the connecting portion is located between the most detailed portion and the rocking edge portion in the radial direction. .

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