WO2011061834A1 - 伝動ベルト - Google Patents
伝動ベルト Download PDFInfo
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- WO2011061834A1 WO2011061834A1 PCT/JP2009/069647 JP2009069647W WO2011061834A1 WO 2011061834 A1 WO2011061834 A1 WO 2011061834A1 JP 2009069647 W JP2009069647 W JP 2009069647W WO 2011061834 A1 WO2011061834 A1 WO 2011061834A1
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- WIPO (PCT)
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- ring
- saddle surface
- central portion
- curvature
- width direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G5/00—V-belts, i.e. belts of tapered cross-section
- F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
Definitions
- the present invention relates to an improvement in a transmission belt comprising an endless annular hoop in which a plurality of thin strip-shaped rings are overlapped and a large number of elements supported by the hoop in a state of being annularly linked along the hoop. is there.
- the transmission belt described in Patent Document 1 is an example thereof, and the saddle surface has a curved shape in which the central portion in the width direction is convex outward, and the first ring is curved in the pressed state.
- the inner peripheral surface is brought into close contact with the saddle surface over substantially the entire width direction.
- the width direction of the saddle surface is the same direction as the width direction of the thin strip-shaped first ring.
- FIG. 7 is a view for explaining an example of such a conventional transmission belt, and schematically showing an engagement state between the first ring 102 located on the innermost periphery of the hoop 100 and the saddle surface 106 of the element 104. It is the cross-sectional shape in the width direction of the thin ring-shaped first ring 102.
- the saddle surface 106 has a constant radius of curvature Rs centered on the center of curvature Ps on the center line S defined substantially at the center in the width direction, and the central portion is gently convex in a convex shape outward, that is, on the outer peripheral side (upward in FIG. 7). It has a curved shape that bulges out.
- the first ring 102 has a radius of curvature Rr larger than the radius of curvature Rs, as shown by the alternate long and short dash line, and has a curved shape in which the central portion gently bulges outward in a convex shape. Since the wound portion is pressed against the saddle surface 106 by tension, it is elastically deformed following the curved shape of the saddle surface 106 as shown by the solid line, and the inner peripheral surface extends substantially over the entire width direction. 106. Note that the position of the first ring 102 in the width direction is automatically adjusted so that the center of curvature Pr is substantially located on the center line S of the saddle surface 106. In addition, since all of FIG. 7 is a cross section, hatching (slant lines) representing the cross section is omitted.
- the present invention has been made against the background described above, and its object is to provide a space between the center portion in the width direction on the inner peripheral surface of the first ring located at the innermost periphery of the hoop and the saddle surface. It is to improve the lubrication performance.
- the first invention comprises: (a) an endless annular hoop in which a plurality of thin strip-like rings are overlapped; and (b) a hoop supported in an annular form along the hoop. And a plurality of elements having saddle surfaces pressed against the inner peripheral surface of the first ring located at the innermost periphery of the hoop, and (c) wound around a plurality of pulleys.
- the transmission belt that transmits power
- the shape of the first ring in the width direction is elastically deformed following the saddle surface.
- a gap is formed between the saddle surface and the central portion in the width direction on the inner peripheral surface of the first ring in the pressed state.
- the second invention comprises (a) an endless annular hoop in which a plurality of thin strip-like rings are overlapped, and (b) a ring supported along the hoop in a state of being annularly linked.
- a plurality of elements having a saddle surface pressed against the inner peripheral surface of the first ring located on the inner periphery, and (c) wound around a plurality of pulleys to transmit power,
- the shape of the first ring in the width direction is elastically deformed following the saddle surface.
- D ⁇
- the saddle surface is As a whole, the central portion in the width direction is curved so as to bulge, and the degree of bulging of the central portion is smaller than the degree of bulging of the peripheral portions on both sides.
- the peripheral portion of the saddle surface is curved with a predetermined curvature, and the central portion has a curvature smaller than the curvature of the peripheral portion. It is characterized by that.
- the curvature can be paraphrased by the radius of curvature, and the fact that the curvature of the central portion is smaller than the curvature of the peripheral portion means that the curvature radius Rs1 of the central portion is larger than the curvature radius Rs2 of the peripheral portion.
- the first ring is elastically deformed so that both side portions in the width direction are in close contact with the peripheral portion of the saddle surface in the pressed state.
- the overall shape is a curved shape in which the central portion in the width direction bulges, and a gap is formed between the saddle surface and the central portion in the width direction.
- a fifth invention is characterized in that, in the transmission belt according to any one of the second to fourth inventions, the degree of bulging of the central portion of the saddle surface is 0, and is linear in the width direction. To do. Note that the degree of bulging of the central portion is 0 is the same as the curvature radius Rs1 of the central portion being ⁇ (infinite).
- the transmission belt of the first invention in a pressed state in which the inner peripheral surface of the first ring is pressed against the saddle surface, there is a gap between the center portion in the width direction on the inner peripheral surface of the first ring and the saddle surface. Since it is formed, the lubricating oil is held in the gap, and the lubricating performance of the central portion is improved to suppress wear and seizure. As a result, the durability of the transmission belt can be improved, or the amount of lubricating oil to be supplied can be reduced, and the required capacity of the oil pump is reduced and the efficiency is improved.
- the peripheral part is also well lubricated by the lubricating oil retained in the central part of the gap. Lubrication performance is improved and wear and seizure are suppressed.
- the saddle surface is curved so that the central portion in the width direction bulges as a whole, and the degree of bulging of the central portion (the curvature of the arc, the inclination angle of the straight line, etc.) Since the inner ring surface of the first ring is pressed against the saddle surface, both sides in the width direction of the first ring are in close contact with the peripheral portion of the saddle surface. If the curved shape in which the central portion in the width direction swells as a whole by being elastically deformed, the pressing load with the saddle surface at the central portion is reduced or a gap is generated.
- the central part of the first ring when the degree of bulging of the central part of the first ring is larger than the degree of bulging of the central part of the saddle surface, as in the fourth aspect, the central part is between the first ring and the saddle surface. A gap is formed, and the lubricating oil is held in the gap, and the same effect as the first invention can be obtained.
- the pressure load is higher in the peripheral portion (both side portions of the first ring) than the center portion where the gap is formed, but the load is applied to the first ring substantially uniformly by elastic deformation in the peripheral portion. Since the load is widely dispersed, the load does not act intensively as in the conventional central portion, and the peripheral portion is also well lubricated by the lubricating oil held in the gap in the central portion. As a result, lubrication performance is improved and wear and seizure are suppressed.
- the central portion in the width direction of the first ring is also substantially in contact with the central portion of the saddle surface, and there may be no clear gap formed between them. Since the degree of swelling of the central portion of the saddle surface is smaller than that of the peripheral portion, the pressing load is low even when no gap is formed. For this reason, compared with the conventional case where a load acts on the central portion intensively, the lubricating performance of the central portion is improved and wear and seizure are suppressed.
- the pressing load is high, but in the peripheral part, the first ring is made to adhere substantially uniformly by elastic deformation and the load is widely dispersed, so the load is concentrated as in the conventional central part. Without acting, a predetermined lubricating performance can be obtained also in the peripheral portion, and the lubricating performance is improved as compared with the conventional one.
- the degree of swelling of the central portion of the saddle surface is zero and is linear in the width direction, a relatively large gap is formed between the inner peripheral surface of the first ring. As a result, the lubricating oil is retained in the gaps, so that better lubricating performance can be obtained.
- FIGS. 2A and 2B are diagrams for explaining the transmission belt of FIG. 1, in which FIG. 1A is an enlarged view of a section taken along the line IIA in FIG. 1, and FIG. FIG. 2 (b) is a view corresponding to the section taken along the line III-III in FIG. 2A, (a) is a cross-sectional view showing the engagement state between the saddle surface and the first ring, and (b) is for explaining the shape of the saddle surface. It is sectional drawing which abbreviate
- FIG. 6 is a diagram for explaining still another embodiment of the present invention, wherein (a) and (b) are cross-sectional views corresponding to (a) and (b) ⁇ in FIG. 3, respectively. It is a figure explaining another Example of this invention, and is sectional drawing equivalent to (a) ridge of FIG. It is a figure explaining an example of the conventional power transmission belt, and is sectional drawing equivalent to (a) ridge of FIG.
- the present invention is preferably applied to a transmission belt used in a belt type continuously variable transmission for a vehicle, but is wound around a belt type continuously variable transmission other than for a vehicle and a pair of pulleys having a constant gear ratio.
- the transmission belt can be applied to various transmission belts such as a transmission belt used by being wound around three or more pulleys.
- a pair of concave grooves for accommodating a hoop are provided laterally symmetrically, and the hoops are respectively accommodated in the concave grooves, and the lower side of the concave grooves (the inner peripheral side of the hoop).
- the side wall is configured to function as a saddle surface, various aspects are possible, such as having only a single groove to accommodate a single hoop.
- the saddle surface is curved so that the central part in the width direction bulges as a whole, and the degree of bulging of the central part is made smaller than the degree of bulging of the peripheral part,
- the radius of curvature Rs1 of the central portion is ⁇ (infinite), but may be a finite value larger than the radius of curvature Rs2 of the peripheral portion. It is also possible to make the curvature of the central portion a negative curvature (dent) with respect to the curvature of the peripheral portion.
- the degree of bulging of the peripheral portion located on both sides of the central portion may be the same as each other, but may be different from each other. Further, the degree of bulging of the curvature radii Rs1, Rs2, etc. may be constant, but can be changed continuously. In order to prevent stress concentration when the first ring is pressed, it is desirable that the boundary portion between the central portion and the peripheral portion be smoothly connected by an arc or the like.
- the degree of swelling of the central portion and the peripheral portion of the saddle surface can be expressed by a curvature as in the third invention when the shape in the width direction is an arc, but the swelling of the saddle surface is, for example, a trapezoidal shape.
- a gap may be formed in the central portion as a result.
- the degree of swelling of the saddle surface for example, the radius of curvature Rs may be substantially constant throughout the width direction. That is, the curvature radius Rr of the inner peripheral surface of the first ring may be made smaller than the curvature radius Rs of the saddle surface so that a gap remains in the central portion even in the pressed state.
- the inner peripheral surface of the first ring may substantially contact the central portion.
- the plurality of rings of the hoop have a curved shape in which a central portion in the width direction bulges outward corresponding to the shape of the saddle surface.
- the curvature of the peripheral portion of the saddle surface in the third invention It can be curved with a smaller curvature, but it can also be curved with a curvature substantially the same as the curvature of the peripheral portion of the saddle surface, or with a curvature larger than the curvature of the peripheral portion of the saddle surface.
- FIG. 1 is a perspective view showing a vehicle belt type continuously variable transmission 8 to which the present invention is preferably applied.
- FIG. 2 (a) is an enlarged view of a section taken along the line IIA in FIG. b) is an enlarged view of the right side of one element 26 in (a).
- the belt-type continuously variable transmission 8 includes a pair of pulleys 14 and 16 that have a V-groove 12 having a variable groove width on the outer peripheral portion and are provided to be rotatable around mutually parallel axes.
- the transmission belt 10 is wound around the pulleys 14 and 16.
- the pulleys 14 and 16 include fixed rotating bodies 14a and 16a fixed to the rotating shafts 18 and 19, respectively, and movable rotating bodies 14b and 16b provided so as to be relatively movable in the axial direction with respect to the rotating shafts 18 and 19. I have.
- the opposing surfaces of the fixed rotating body 14a and the movable rotating body 14b and the opposing surfaces of the fixed rotating body 16a and the movable rotating body 16b have a conical shape in which the relative distance in the axial direction increases toward the outer side in the radial direction.
- Each sheave surface 20 is provided.
- the V-shaped groove 12 is formed by the pair of opposed sheave surfaces 20.
- the transmission belt 10 is supported by the pair of endless annular hoops 24 in which a plurality of thin strip-like rings 22 having flexibility are overlapped, and the pair of hoops 24, and along the pair of hoops 24 in the thickness direction.
- a large number of elements 26 made of plate-like metal linked in an annular shape.
- the ring 22 is, for example, a high-strength steel plate having a thickness of about 0.2 mm that is formed into a ring shape, and is stacked in layers, for example, from the inside to the outside.
- the element 26 is a thick plate-like piece formed by punching a steel plate having a thickness of about 1.8 mm, for example, and is provided with about 400 in this embodiment. As shown in FIG.
- the element 26 has a pair of contact surfaces 28 that are in contact with each other while facing the pair of sheave surfaces 20, respectively, and both sides thereof are open to the sides.
- a pair of concave grooves 30 are provided symmetrically, and the hoops 24 are respectively accommodated in the concave grooves 30, so that a number of elements 26 are connected in an annular shape by the pair of hoops 24. Supported by the state.
- the power transmission belt 10 is wound around a pair of pulleys 14 and 16 and rotated in the circumferential direction, whereby power is transmitted between the pulleys 14 and 16.
- the hoop 24 is wall surface on the inner peripheral side of the concave groove 30.
- the saddle surface 32 is pressed, and the shape of the hoop 24 in the width direction is elastically deformed following the shape of the saddle surface 32.
- 3A is a cross-sectional view showing an engagement state between the first ring 22a located on the innermost periphery of the hoop 24 and the saddle surface 32, and a pair of hoops in a cross section taken along the line III-III in FIG. One (right side) of 24 is expanded and shown.
- 3B is a cross-sectional view showing the shape of the saddle surface 32 with the hoop 24 omitted. Since all of (a) and (b) ⁇ in FIG. 3 are cross-sections, hatches (diagonal lines) meaning cross-sections are omitted. The same applies to FIGS. 4 to 6 below.
- the saddle surface 32 includes a central portion E2 located substantially at the center in the width direction (left-right direction in the figure) and peripheral portions E1 and E3 located on both sides of the central portion E2. It is divided. As a whole, the central portion E2 has a curved shape that gently bulges outwardly, that is, on the outer peripheral side (above FIG. 3 (b)), and the curvature of the central portion E2 is the peripheral portion E1 on both sides. , Which is smaller than the curvature of E3.
- the peripheral portions E1 and E3 have an arc shape that gently swells at a common constant radius of curvature Rs2 centered on the center of curvature Ps2 on the center line S defined at the approximate center in the width direction.
- the central portion E2 is formed with a radius of curvature Rs1 larger than the radius of curvature Rs2 centered on the center of curvature Ps1 on the center line S.
- Rs1 ⁇ (infinity)
- the degree of bulging is 0, and the central portion E2 is linear in the width direction.
- a two-dot chain line shown in the central portion E2 is an arc having a radius of curvature Rs2, and the central portion E2 has a concave shape relative to the arc having a radius of curvature Rs2.
- the curvature radius Rs2 is set as appropriate, for example, with the same size as the curvature radius Rs of the saddle surface in the prior art shown in FIG.
- the boundary portions between the central portion E2 and the peripheral portions E1 and E3 are each smoothly connected by an arc or the like.
- the first ring 22a has a curved shape in which the central portion gently bulges outwardly in a convex shape with a radius of curvature Rr larger than the radius of curvature Rs2 as shown by a dashed line in FIG. Arc-shaped), but in the pressed state where the portions wound around the pulleys 14 and 16 are pressed against the saddle surface 32 by tension, both sides in the width direction are the periphery of the saddle surface 32 as shown by the solid line.
- the entire central portion in the width direction has a curved shape that bulges gently.
- the curved shape in this case is an arc shape having substantially the same curvature radius as the curvature radius Rs2 of the peripheral portions E1 and E3 of the saddle surface 32.
- the inner peripheral surface of the first ring 22a is formed into an arc shape having substantially the same radius of curvature as the radius of curvature Rs2, so that it closely contacts the peripheral portions E1 and E3 of the saddle surface 32 on both sides in the width direction.
- a predetermined gap (shaded portion) 34 is formed due to the difference from the radius of curvature Rs1 of the central portion E2 of the saddle surface 32, and the lubricating oil is held in the gap 34.
- the saddle surface 32 is curved so that the central portion E2 in the width direction bulges as a whole, and the curvature (degree of bulging) of the central portion E2 is increased. ) Is smaller than the curvatures of the peripheral portions E1 and E3 (Rs2 ⁇ Rs1). Therefore, in the pressing state in which the inner peripheral surface of the first ring 22a is pressed against the saddle surface 32, the width of the first ring 22a is increased.
- the central portion in the width direction is bulged as a whole, and the curvature of the central portion of the saddle surface 32 is It is made larger than the curvature of the central portion E2. Due to the difference in curvature of the central portion, a gap 34 is formed between the inner peripheral surface of the first ring 22a and the saddle surface 32 in the central portion, so that the lubricating oil is held in the gap 34.
- the lubrication performance of the central portion is improved and wear and seizure are suppressed. As a result, the durability of the transmission belt 10 is improved, or the amount of lubricating oil to be supplied can be reduced, and the required capacity of the oil pump is reduced and the efficiency is improved.
- the peripheral portion E1 and E3 other than the central portion E2 where the gap 34 is formed has a higher pressing load than the conventional portion, but in the peripheral portions E1 and E3, the first ring 22a is elastically deformed to make the saddle surface 32 substantially uniform. Since the load is widely dispersed by being in close contact with the center portion, the load is not concentrated by point contact unlike the central portion (near the center line S) of the conventional apparatus shown in FIG. Since the peripheral portions E1 and E3 are also well lubricated by the retained lubricating oil, the overall lubrication performance is improved and wear and seizure are suppressed.
- the radius of curvature Rs1 of the central portion E2 of the saddle surface 32 is ⁇ and is linear in the width direction. Therefore, a relatively large gap 34 is formed between the inner peripheral surface of the first ring 22a. Is formed, and the lubricating oil is held in the gap 34, whereby a better lubricating performance can be obtained.
- FIG. 4 is a cross-sectional view corresponding to FIG. 3 (b), and the shape of the saddle surface 40 is different from that of the first embodiment. That is, the peripheral portions E1 and E3 of the saddle surface 40 of the second embodiment have an arc shape that gently swells at a common constant radius of curvature Rs2 as in the first embodiment, but the central portion E2
- the radius of curvature Rs1 is a finite value larger than the radius of curvature Rs2, and the central portion E2 has an arc shape that bulges outward in a convex shape.
- the first ring 22a pressed against the saddle surface 40 is elastically deformed into an arc shape having substantially the same curvature radius as the curvature radius Rs2 of the peripheral portions E1 and E3 of the saddle surface 40.
- a predetermined gap 34 is formed by the difference from the curvature radius Rs1 of the central portion E2 of the saddle surface 40, and the lubricating oil is well held in the gap 34. Similar effects can be obtained.
- the width of the first ring 22a is increased.
- the central portion is also substantially brought into contact with the saddle surface 40, and a clear gap 34 may not be formed between them.
- the radius of curvature Rs1 of the central portion E2 of the saddle surface 40 is smaller than the radius of curvature Rs2 of the peripheral portions E1 and E3, and is recessed from the arc (two-dot chain line) of the radius of curvature Rs2. Even when it is not formed, the pressing load is reduced.
- the lubricating performance of the central portion E2 is improved and wear and seizure are suppressed.
- the pressing load is high in the peripheral portions E1 and E3 other than the central portion E2, in the peripheral portions E1 and E3, the first ring 22a is brought into substantially uniform contact by elastic deformation and the load is widely dispersed. The load does not act intensively as in the central portion, and the predetermined lubricating performance can be obtained for the peripheral portions E1 and E3. Overall, the lubricating performance is improved as compared with the conventional portion.
- FIGS. 3A and 3B are cross-sectional views corresponding to FIGS. 3A and 3B, respectively, and the shape of the saddle surface 42 is different from that of the first embodiment. That is, the saddle surface 42 of the third embodiment has a curved shape in which the central portion E2 as a whole gradually bulges in a convex shape to the outside, that is, the outer peripheral side (above FIG. 5 (b)). Although it is the same as Example 1, the center part E2 and the peripheral parts E1 and E3 are all formed of a straight line, and the point which has comprised the trapezoid shape as a whole differs.
- both side portions of the first ring 22a are elastically deformed so as to be in close contact with the peripheral portions E1 and E3 of the saddle surface 42.
- the entire central portion in the width direction bulges out as shown by the solid line, so that a gap 44 is formed in the central portion as in the first embodiment.
- the boundary portions between the central portion E2 and the peripheral portions E1 and E3 of the saddle surface 42 are all smoothly connected by an arc or the like.
- the saddle surface 42 may be divided into four or more parts and connected in a polygonal line shape to form a gently bulging curved shape.
- the first ring 22a does not completely adhere to the saddle surface 46 due to the rigidity of the first ring 22a, and a gentle curved shape is maintained as shown by a solid line, and a gap (shaded portion) is formed in the central portion in the width direction. 48) is left.
- the lubricating oil is held in the gap 48, so that the same effect as that of the first embodiment can be obtained.
- both end portions of the first ring 22a are pressed against the saddle surface 46 in a state close to point contact. Therefore, compared to the first to third embodiments, the pressing load is applied to the contact portions of both end portions. However, since the contact portion at both ends is well lubricated by the lubricating oil held in the gap 48 in the central portion, the lubrication performance is improved as a whole compared with the conventional device shown in FIG. Wear and seizure are suppressed.
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Abstract
Description
なお、この明細書でサドル面の幅方向とは、薄板帯状の第1リングの幅方向と同じ方向のことである。
なお、曲率を曲率半径で言い換えることも可能で、中央部分の曲率が周辺部分の曲率よりも小さいことは、中央部分の曲率半径Rs1が周辺部分の曲率半径Rs2よりも大きいことを意味する。
なお、中央部分の膨出の程度が0であることは、中央部分の曲率半径Rs1が∞(無限大)であることと同じである。
図1は、本発明が好適に適用される車両用ベルト式無段変速機8を示す斜視図で、図2の(a) は図1におけるIIA 矢視部断面の拡大図、図2の(b) は(a) における一つのエレメント26の右側面拡大図である。ベルト式無段変速機8は、溝幅が可変であるV溝12を外周部に有して互いに平行な軸心まわりに回転可能に設けられた一対のプーリ14、16を備えており、それ等のプーリ14、16に跨がって伝動ベルト10が巻き掛けられている。プーリ14、16は、それぞれ回転軸18、19に固定された固定回転体14a、16aと、回転軸18、19に対して軸方向に相対移動可能に設けられた可動回転体14b、16bとを備えている。これら固定回転体14aおよび可動回転体14bの相対向する面、および固定回転体16aおよび可動回転体16bの相対向する面には、径方向外側に向かうに従って軸方向の相対距離が大きくなる円錐状のシーブ面20がそれぞれ設けられている。上記V溝12は、これら一対の相対向するシーブ面20により形成されている。
Claims (5)
- 薄板帯状のリングが複数重ね合わされた無端環状のフープと、
該フープに沿って環状に連ねられた状態で該フープにより支持されるとともに、該フープの最内周に位置する第1リングの内周面に押圧されるサドル面を備えている多数のエレメントと
を有し、複数のプーリ間に巻き掛けられて動力を伝達するとともに、前記第1リングの内周面が前記サドル面に押圧される押圧状態では、該第1リングの幅方向の形状が該サドル面に倣って弾性変形させられる伝動ベルトにおいて、
前記押圧状態で前記第1リングの内周面における幅方向の中央部分と前記サドル面との間に隙間が形成される
ことを特徴とする伝動ベルト。 - 薄板帯状のリングが複数重ね合わされた無端環状のフープと、
該フープに沿って環状に連ねられた状態で該フープにより支持されるとともに、該フープの最内周に位置する第1リングの内周面に押圧されるサドル面を備えている多数のエレメントと
を有し、複数のプーリ間に巻き掛けられて動力を伝達するとともに、前記第1リングの内周面が前記サドル面に押圧される押圧状態では、該第1リングの幅方向の形状が該サドル面に倣って弾性変形させられる伝動ベルトにおいて、
前記サドル面は、全体として幅方向の中央部分が膨出するように湾曲させられているとともに、該中央部分の膨出の程度は両側の周辺部分の膨出の程度に比較して小さい
ことを特徴とする伝動ベルト。 - 前記サドル面の前記周辺部分はそれぞれ所定の曲率で湾曲させられているとともに、前記中央部分は該周辺部分の曲率よりも小さな曲率とされている
ことを特徴とする請求項2に記載の伝動ベルト。 - 前記第1リングは、前記押圧状態において幅方向の両側部が前記サドル面の前記周辺部分に密着するように弾性変形させられることにより、全体として幅方向の中央部分が膨出する湾曲形状とされ、該幅方向の中央部分で該サドル面との間に隙間が形成される
ことを特徴とする請求項2または3に記載の伝動ベルト。 - 前記サドル面の前記中央部分の膨出の程度は0で、幅方向において直線状を成している
ことを特徴とする請求項2~4の何れか1項に記載の伝動ベルト。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN200980162534.1A CN102667232B (zh) | 2009-11-19 | 2009-11-19 | 传动带 |
PCT/JP2009/069647 WO2011061834A1 (ja) | 2009-11-19 | 2009-11-19 | 伝動ベルト |
US13/510,804 US8870695B2 (en) | 2009-11-19 | 2009-11-19 | Transmission belt |
JP2011541764A JP5246344B2 (ja) | 2009-11-19 | 2009-11-19 | 伝動ベルト |
DE112009005554.0T DE112009005554B3 (de) | 2009-11-19 | 2009-11-19 | Übertragungsriemen |
DE112009005389T DE112009005389T5 (de) | 2009-11-19 | 2009-11-19 | Übertragungsriemen |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2009/069647 WO2011061834A1 (ja) | 2009-11-19 | 2009-11-19 | 伝動ベルト |
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WO2011061834A1 true WO2011061834A1 (ja) | 2011-05-26 |
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PCT/JP2009/069647 WO2011061834A1 (ja) | 2009-11-19 | 2009-11-19 | 伝動ベルト |
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US (1) | US8870695B2 (ja) |
JP (1) | JP5246344B2 (ja) |
CN (1) | CN102667232B (ja) |
DE (1) | DE112009005389T5 (ja) |
WO (1) | WO2011061834A1 (ja) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL1039980C2 (en) * | 2012-12-28 | 2014-07-03 | Bosch Gmbh Robert | Transverse segment for a drive belt with a carrier ring and multiple transverse segments. |
US9423002B2 (en) * | 2013-05-28 | 2016-08-23 | Kyocera Document Solutions Inc. | Metal belt and driving mechanism with same metal belt |
JP6506062B2 (ja) * | 2015-03-24 | 2019-04-24 | 本田技研工業株式会社 | 無段変速機用金属エレメントの製造方法 |
NL1041657B1 (en) * | 2015-12-30 | 2017-07-11 | Bosch Gmbh Robert | Method for assembling a set of nested steel flexible rings and a drive belt provided there with. |
US20190154112A1 (en) * | 2016-02-12 | 2019-05-23 | Aisin Aw Co., Ltd. | Power transfer belt |
DE112017000181T5 (de) * | 2016-02-12 | 2018-07-19 | Aisin Aw Co., Ltd. | Übertragungsriemen |
CN109073043B (zh) * | 2016-05-18 | 2020-12-15 | 爱信艾达株式会社 | 传动带 |
JP6809368B2 (ja) * | 2017-05-16 | 2021-01-06 | アイシン・エィ・ダブリュ株式会社 | 無段変速機および伝動ベルト |
JP6859915B2 (ja) * | 2017-10-10 | 2021-04-14 | トヨタ自動車株式会社 | 伝動ベルト |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5917350U (ja) * | 1982-07-23 | 1984-02-02 | トヨタ自動車株式会社 | 伝導ベルト |
JPS61162636U (ja) * | 1985-03-29 | 1986-10-08 | ||
JPH0519704U (ja) * | 1991-08-22 | 1993-03-12 | 三ツ星ベルト株式会社 | 高負荷伝動用ベルト |
WO2005019684A1 (ja) * | 2003-08-26 | 2005-03-03 | Fukuju Kogyo Kabushiki Kaisha | 金属ベルト及びそれに使用する押しゴマ |
Family Cites Families (43)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3720113A (en) * | 1971-04-06 | 1973-03-13 | Doorne H Van | Flexible continuous power transmission means |
NL168742C (nl) * | 1978-01-31 | 1983-09-16 | Volvo Car Bv | Werkwijze voor het vormen van gewelfde drijfbandoplegvlakken op de dwarselementen van een transmissieband, alsmede schuurband voor het uitvoeren van deze werkwijze. |
NL7900435A (nl) * | 1979-01-19 | 1980-07-22 | Doornes Transmissie Bv | Samengestelde drijfriem met dwarselementen voorzien van onderlinge koppelingsmiddelen. |
US4386921A (en) * | 1980-04-28 | 1983-06-07 | Borg-Warner Corporation | Metal power transmission belt |
US4526559A (en) * | 1981-03-25 | 1985-07-02 | Borg-Warner Corporation | Tension-type belt/pulley system for a continuously variable transmission |
JPS5917350A (ja) | 1982-07-22 | 1984-01-28 | テルモ株式会社 | 医療用包装容器 |
JPS5919745A (ja) * | 1982-07-23 | 1984-02-01 | Toyota Motor Corp | トルク伝導装置用駆動ベルト |
US4533342A (en) * | 1983-06-06 | 1985-08-06 | Dayco Corporation | Belt construction for a continuously variable transmission, transverse belt element therefor and methods of making the same |
US4676768A (en) * | 1983-06-06 | 1987-06-30 | Dayco Products, Inc. | Belt construction for a continuously variable transmission, transverse belt element therefor and methods of making the same |
US4617007A (en) * | 1983-06-06 | 1986-10-14 | Dayco Corporation | Belt construction for a continuously variable transmission, transverse belt element therefor and methods of making the same |
US4610648A (en) * | 1983-10-31 | 1986-09-09 | Dayco Corporation | Belt construction for a continuously variable transmission, transverse belt element therefor and methods of making the same |
JPS60192146A (ja) * | 1984-03-14 | 1985-09-30 | Toyota Motor Corp | 動力伝達用無端ベルト |
JPS61162636A (ja) | 1985-01-11 | 1986-07-23 | Kenichi Sasaki | 布基礎用ブロツクおよび同ブロツクを使用した布基礎施工方法 |
JPS63115937A (ja) * | 1986-10-30 | 1988-05-20 | Fuji Heavy Ind Ltd | 無段変速機用vベルト |
FR2625783B1 (fr) * | 1988-01-11 | 1990-05-11 | Caoutchouc Manuf Plastique | Organe de transmission pour variateur continu de vitesse, a maillons transversaux poussants et ame souple, fonctionnant par frottement sec |
NL8802546A (nl) * | 1988-10-17 | 1990-05-16 | Doornes Transmissie Bv | Drijfriem en dwarselement voor een dergelijke drijfriem alsmede een werkwijze voor de vervaardiging van het dwarselement. |
NL8900266A (nl) * | 1989-02-03 | 1990-09-03 | Doornes Transmissie Bv | Overbrenging voorzien van een drijfriem en v-vormige poelies. |
JP2529017B2 (ja) * | 1990-07-25 | 1996-08-28 | 日産自動車株式会社 | 伝動ベルト |
JPH0519704A (ja) | 1991-07-16 | 1993-01-29 | Tokyo Electric Co Ltd | 回転式表示装置 |
NL9200537A (nl) * | 1992-03-24 | 1993-10-18 | Doornes Transmissie Bv | Dwarselement voor een drijfriem. |
JPH10103429A (ja) * | 1996-09-30 | 1998-04-21 | Mazda Motor Corp | 歯車式変速機構造 |
JP3554490B2 (ja) * | 1998-09-25 | 2004-08-18 | 本田技研工業株式会社 | 無段変速機用ベルト |
ATE282783T1 (de) * | 1999-07-27 | 2004-12-15 | Doornes Transmissie Bv | Treibriemen und getriebe worin gleiches verwendet ist |
US6830525B1 (en) * | 1999-09-15 | 2004-12-14 | Van Doorne's Transmissie B.V. | Belt |
DE69925283T2 (de) | 1999-12-20 | 2006-01-19 | Van Doorne's Transmissie B.V. | Treibriemen für ein stufenlos regelbares Getriebe, endloses Band dafür und Herstellungsverfahren solch eines Bandes |
JP3669680B2 (ja) * | 2000-01-17 | 2005-07-13 | 本田技研工業株式会社 | 無段変速機用ベルト |
JP3406283B2 (ja) * | 2000-08-11 | 2003-05-12 | 本田技研工業株式会社 | 無段変速機用ベルト |
JP2002168305A (ja) | 2000-11-30 | 2002-06-14 | Mitsubishi Motors Corp | 無段変速機用ベルトのエレメント、及び無段変速機用ベルト |
EP1352182B1 (en) * | 2000-12-28 | 2004-11-10 | Van Doorne's Transmissie B.V. | Belt |
EP1219860B1 (en) * | 2000-12-28 | 2010-03-03 | Bosch Transmission Technology b.v. | Belt |
EP1221561A1 (en) * | 2000-12-28 | 2002-07-10 | Van Doorne's Transmissie B.V. | Belt |
DE60111718T2 (de) * | 2001-03-19 | 2006-05-04 | Van Doorne's Transmissie B.V. | Metallschubriemen und Material dafür |
DE60112737T2 (de) * | 2001-07-02 | 2006-03-30 | Van Doorne's Transmissie B.V. | Treibriemen, Herstellungsverfahren eines endlosen Bandes dafür, und dieses ver wendendes, stufenlos regelbares Getriebe |
JP2003056649A (ja) * | 2001-08-10 | 2003-02-26 | Honda Motor Co Ltd | 無段変速機用ベルト |
JP3912150B2 (ja) | 2002-03-18 | 2007-05-09 | 日産自動車株式会社 | 無段変速機用ベルト |
JP3861824B2 (ja) * | 2003-02-13 | 2006-12-27 | トヨタ自動車株式会社 | 無端金属リングの周長調整装置および周長調整方法 |
EP1544502B1 (en) | 2003-12-18 | 2011-08-10 | Robert Bosch Gmbh | Drive belt |
US7294077B2 (en) * | 2004-02-24 | 2007-11-13 | General Motors Corporation | CVT belt with chromium nitride coating |
JP4820411B2 (ja) | 2005-07-29 | 2011-11-24 | ロベルト ボッシュ ゲゼルシャフト ミト ベシュレンクテル ハフツング | 駆動ベルト |
JP4667342B2 (ja) * | 2006-11-07 | 2011-04-13 | 株式会社豊田中央研究所 | 動力伝達用無端ベルト |
JP4710900B2 (ja) * | 2007-12-18 | 2011-06-29 | トヨタ自動車株式会社 | ベルト用エレメントおよび伝動ベルト |
CN101910678B (zh) | 2007-12-24 | 2013-02-06 | 罗伯特·博世有限公司 | 传动皮带 |
JP2009269547A (ja) | 2008-05-09 | 2009-11-19 | Mazda Motor Corp | ハイブリッド車両 |
-
2009
- 2009-11-19 JP JP2011541764A patent/JP5246344B2/ja not_active Expired - Fee Related
- 2009-11-19 US US13/510,804 patent/US8870695B2/en active Active
- 2009-11-19 CN CN200980162534.1A patent/CN102667232B/zh not_active Expired - Fee Related
- 2009-11-19 DE DE112009005389T patent/DE112009005389T5/de not_active Ceased
- 2009-11-19 WO PCT/JP2009/069647 patent/WO2011061834A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5917350U (ja) * | 1982-07-23 | 1984-02-02 | トヨタ自動車株式会社 | 伝導ベルト |
JPS61162636U (ja) * | 1985-03-29 | 1986-10-08 | ||
JPH0519704U (ja) * | 1991-08-22 | 1993-03-12 | 三ツ星ベルト株式会社 | 高負荷伝動用ベルト |
WO2005019684A1 (ja) * | 2003-08-26 | 2005-03-03 | Fukuju Kogyo Kabushiki Kaisha | 金属ベルト及びそれに使用する押しゴマ |
Also Published As
Publication number | Publication date |
---|---|
JPWO2011061834A1 (ja) | 2013-04-04 |
CN102667232B (zh) | 2014-07-23 |
JP5246344B2 (ja) | 2013-07-24 |
CN102667232A (zh) | 2012-09-12 |
DE112009005389T5 (de) | 2012-09-13 |
US20120231910A1 (en) | 2012-09-13 |
US8870695B2 (en) | 2014-10-28 |
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