JP2016205522A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission including a loading cam type pressing device capable of sufficiently lubricating a cam surface and the surface of a cam roller with oil.SOLUTION: In a loading cam type pressing device 100 of a toroidal type continuously variable transmission, since at a gap between a cam surface 111 of a loading cam 101 and a holder 102, and at a gap between a cam surface 110 of an input side disc 2 and the holder 102, an oil amount control plate 104 is provided respectively, most of the gap is filled by the oil amount control plate 104, and oil is guided to the cam surfaces 110, 111 and the surface of a cam roller 103 thereby to enable these surfaces to be sufficiently lubricated by oil.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

For example, as a double-cavity toroidal continuously variable transmission used as a transmission for automobiles, the one described in FIGS. 5 and 6 is known.
This double cavity type toroidal continuously variable transmission is configured as shown in FIGS. As shown in FIG. 5, the input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is driven to rotate by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in the drawing. It has become. The output gear 4 is supported in the casing 50 via an intermediate wall 13 formed by coupling two members, whereby the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O Directional displacement is prevented.

As shown in FIG. 7, the pressing device 12 includes a loading cam 46 that rotates together with a drive shaft (not shown), and a plurality of cam rollers 48 that are rotatably held by a holder 47. On one side of the loading cam 46 (the right side in FIG. 7), a cam surface 46a, which is a concavo-convex portion (wave-like portion) extending in the circumferential direction, is formed, and on the outer side surface (the left side in FIG. 7) of the input side disk 2. Also, a cam surface 2d having a similar shape is formed.
An oil hole 224 is provided in the vicinity of the bottom of the loading cam 46, and the oil hole 224 is used for lubricating oil supplied to the ball bearing 210 through the axial hole 220 of the input shaft 1 and the oil hole 222 perpendicular thereto. It acts to supply to the cam roller 48 by the centrifugal force accompanying the rotation of the input shaft 1.

  As shown in FIG. 5, the output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 and rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. A power roller is provided between the inner side surfaces (concave surface; also referred to as a traction surface) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output disks 3 and 3. 11 (see FIG. 6) is rotatably held.

  A step 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 5, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (right surface in FIG. 5) of the input side disk 2 is abutted against a loading nut 9 screwed into a screw portion formed on the outer peripheral surface of the input shaft 1. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and a pressing portion (preload) is applied to a contact portion between the peripheral surfaces 11a and 11a of the power rollers 11 and 11.

  6 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 6, a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In addition, illustration of the input shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is a pair of bent wall portions 20, 20 formed at both ends in the longitudinal direction (vertical direction in FIG. 6) of the support plate portion 16 so as to be bent toward the inner surface side of the support plate portion 16. have. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the center portion of the support plate portion 16, and a base end portion (first shaft portion) 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. Further, each power roller 11 is rotatably supported around the tip end portion (second shaft portion) 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  Further, the pivot shafts 14, 14 of the trunnions 15, 15 are supported so as to be swingable with respect to the pair of yokes 23A, 23B and displaceable in the axial direction (vertical direction in FIG. 6). The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 5), and the inner peripheral surface of the locking hole 19 is a cylindrical surface. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder (cylinder body) 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, when the power rollers 11, 11 tend to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the loading cam type pressing device 12. However, an excessive force is not applied to each component member, and this displacement is absorbed.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (thrust bearing) 24 that is a thrust rolling bearing is sequentially formed from the outer surface side of the power roller 11. A thrust needle bearing 25 is provided. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of such thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds each of the rolling elements 26, 26 in a rollable manner, And an annular outer ring 28. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 6) of the trunnions 15 and 15, respectively, and driving pistons ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 and 2 via the loading cam type pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

  When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 6 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure.

  As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  By the way, in such a loading cam type pressing device in a toroidal type continuously variable transmission, when the cam roller rolls on the cam surface, there is a difference in the amount of movement accompanying rolling in the radial direction of the loading cam. There is a problem that rolling and sliding motion occurs and the cam roller and the surface of the cam surface are easily damaged by fretting wear or the like.

In order to prevent such surface damage due to fretting wear or the like, it is effective to sufficiently lubricate the cam surface and the surface of the cam roller with oil, and a toroidal stepless type equipped with a loading cam type pressing device having a lubricating means. As a transmission, the thing of patent documents 1-4 is known, for example.
In the toroidal type continuously variable transmission described in Patent Document 1, the loading cam includes a cam roller, a holding member that holds the cam roller and restricts the position thereof, and a cam roller that is linked to the side surface of the holding member and around the cam roller. It has the structure which has the cover which forms the oil path which supplies the oil for lubrication.

  In addition, in the toroidal type continuously variable transmission described in Patent Document 2, in the loading cam type pressing device, the cage has an annular main body that fits on the outer periphery of a predetermined portion of the loading cam. An oil groove communicating with a lubricating oil supply oil hole formed in the loading cam is formed over the entire circumference on the peripheral surface, and the oil groove passes through a plurality of oil passages formed in the cage. Through the cam roller and each cam surface in the vicinity of the contact portion, and the side wall in the radially inner portion of the cage where the oil groove and the oil passage are formed forms a shape corresponding to the shape of the cam surface. The structure is opposite to the surface.

  Further, in the toroidal type continuously variable transmission described in Patent Document 3, in the loading cam type pressing device, the cage has an annular main body fitted on the outer periphery of a predetermined portion of the loading cam, and the outer periphery of the main body In addition, a cylindrical portion that overlaps with the outer peripheral surface of the outer disk and the outer peripheral surface of the loading cam is provided, and a sealing portion for lubricating oil is formed by the outer disk, the loading cam, and the cylindrical portion.

  Further, in the toroidal type continuously variable transmission described in Patent Document 4, in the loading cam type pressing device, an oil reservoir for immersing a cam roller provided between the loading cam and the input disk covers an outer peripheral portion of the pressing device. It is the structure provided by such a kite.

JP-A-9-291999 Japanese Patent No. 2006-2882 JP 2013-1000088 A1 Japanese Patent Publication No. 6-72656

  By the way, in the toroidal type continuously variable transmission described in Patent Document 1, relatively large gaps remain between the cage and the cam surface of the loading cam and between the cage and the cam surface of the input side disk. Therefore, the oil ejected toward the cam roller goes to a region where the cam roller does not exist, and there is a possibility that the cam surface and the surface of the cam roller cannot be sufficiently lubricated with oil.

Further, in the toroidal type continuously variable transmission described in Patent Document 2, as in the toroidal type continuously variable transmission described in Patent Document 1, between the cage and the cam surface of the loading cam and between the cage and the input side disk. Since a relatively large gap remains between the cam surface and the oil jetted toward the cam roller, the oil may go to the area where the cam roller does not exist, and the cam surface and the surface of the cam roller may not be sufficiently lubricated by the oil. is there.
Further, since the oil cannot be retained after the oil is guided to the cam roller side, the cam surface and the surface of the cam roller cannot be sufficiently lubricated with the oil, and the oil supply efficiency may be reduced.

  Further, in the toroidal type continuously variable transmission described in Patent Document 3, a cylindrical portion that covers the outer peripheral portion of the loading cam is provided so that the oil is sealed around the cam roller. However, since it has an oil-tight structure, centrifugal hydraulic pressure is generated, and there is a possibility that an axial force is generated more than necessary particularly in a high rotation state, resulting in over-pressing.

Further, in the toroidal type continuously variable transmission described in Patent Document 4, like the toroidal type continuously variable transmission described in Patent Documents 1 and 2, between the cage and the cam surface of the loading cam and between the cage and the input side. Since a relatively large gap remains between the cam surface of the disc, the oil sprayed toward the cam roller goes to a region where the cam roller does not exist, and the cam surface and the surface of the cam roller cannot be sufficiently lubricated with oil. In addition, since the oil cannot be retained after the oil is guided to the cam roller side, the cam surface and the surface of the cam roller cannot be sufficiently lubricated with the oil, and the oil supply efficiency may be reduced. There is also.
Further, since the flange is provided so as to cover the outer peripheral portion of the loading cam type pressing device, there is a possibility that a large load is applied to the flange due to the centrifugal force and it is damaged.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a toroidal continuously variable transmission provided with a loading cam type pressing device capable of sufficiently lubricating the cam surface and the surface of the cam roller with oil. .

In order to achieve the above object, a toroidal continuously variable transmission according to the present invention includes a first disk and a second disk that are concentrically and rotatably provided with their inner surfaces facing each other. And a power roller sandwiched between the two disks and a pressing device that presses the disks in a direction approaching each other. The pressing device includes a loading cam, a cam surface of the loading cam, and the first surface. In a toroidal type continuously variable transmission having a cam roller that is rotatably held by a cage between a cam surface of a disc,
An oil amount control plate is provided in a gap between at least one of the cam surface of the loading cam and the cam surface of the first disk and the cage.

In the present invention, since the oil amount control plate is provided in the gap between at least one of the cam surface of the loading cam and the cam surface of the first disk and the cage, Most of the oil is filled with the oil amount control plate, and the oil is guided to the cam surface and the surface of the cam roller so that they can be sufficiently lubricated by the oil.
Moreover, the weight increase of a press apparatus can be suppressed by forming an oil amount control board with a material whose specific gravity is smaller than steel materials, such as resin.

  According to the present invention, since the oil amount control plate is provided in the gap between the cam surface and the cage, most of the gap is filled with the oil amount control plate and the oil is supplied to the cam surface and the cam roller. They can be guided to the surface and sufficiently lubricated with oil.

1 is a side view of a pressing device, showing a toroidal-type continuously variable transmission according to an embodiment of the present invention. FIG. 2 is an exploded side view of the pressing device. It is a perspective view of the oil quantity control board used for a pressing device equally. The oil quantity control board used for a pressing device is shown, (a) is a front view, (b) is a side view. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG. It is sectional drawing which shows an example of the conventional press apparatus.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
1 is a side view showing a loading cam type pressing device 100 in the toroidal type continuously variable transmission according to the present embodiment, FIG. 2 is an exploded side view of the pressing device 100, and FIG. 3 is used in the pressing device 100. 4 is a perspective view of the oil amount control plate, FIG. 4 shows the oil amount control plate, (a) is a front view, and (b) is a side view.
The toroidal-type continuously variable transmission of the present invention is characterized by the pressing device 100, and the configuration other than the pressing device 100 is the same as that of the prior art. Therefore, the illustration and description thereof are omitted, and the pressing device 100 is described below. To do.

  As shown in FIGS. 1 and 2, the pressing device 100 includes a loading cam 101, a cage 102, a cam roller 103 that is rotatably held by the cage 102, and two oil amount control plates 104 and 104. And a disc spring 105 and a cam surface 110 formed on the back surface of the input side disk 2. The disc spring 105 is used to apply a preload to the input side disk 2.

The loading cam 101 is formed in a disc shape, and includes a disc-shaped cam plate 101a having a cam surface 111 and a cylindrical shaft portion 101b provided at the center of the cam plate 101a. The left end portion of the input shaft 1 is inserted through the shaft portion 101b. An angular ball bearing (angular bearing) (not shown) is interposed between the inner peripheral surface of the shaft portion 101 b and the outer peripheral surface of the input shaft 1. The loading cam 101 is coupled to a drive shaft (not shown). The loading cam 101 is rotated by the rotation of the drive shaft.
The cam surface 111 is formed on the side surface (the right side surface in FIGS. 1 and 2) of the cam plate 101a facing the input side disk 2 in a wavy shape that is uneven in the circumferential direction.
Further, the cam surface 110 on the back surface of the input side disk 2 is formed in a wave shape that is uneven in the circumferential direction, like the cam surface 111.

The cage 102 is formed in the shape of a donut plate, and a fitting portion 102a is provided around the hole in the central portion thereof so as to fit on the outer periphery of the shaft portion 101b of the loading cam 101. A convex portion 102b that projects toward the second side is provided.
Further, on the side surface of the cage 102, four pockets 102c in which the cam roller 103 is rotatably accommodated are provided at predetermined intervals along the circumferential direction.

As shown in FIGS. 3 and 4, the oil amount control plate 104 is formed in a donut plate shape by an elastic material such as resin or rubber, and a pocket in which the cam roller 103 is rotatably accommodated on a side surface thereof. Four 104c are provided at predetermined intervals along the circumferential direction.
Further, a wavy wave surface 104a that is uneven in the circumferential direction is formed on one side surface of the oil amount control plate 104 substantially parallel to the cam surface 110 (111), and the other side surface is a plane orthogonal to the axial direction. It has become.

As shown in FIGS. 1 and 2, such an oil amount control plate 104 includes a gap between the cam surface 111 of the loading cam 101 and the cage 102 and the cam surface 110 and the cage 102 of the input side disk 2. The input shaft 1 is inserted through the central hole of the oil amount control plate 104. The oil amount control plate 104 has at least one of a gap between the cam surface 111 of the loading cam 101 and the cage 102 and a gap between the cam surface 110 of the input side disk 2 and the cage 102. What is necessary is just to provide in a clearance gap.
In this state where the oil amount control plate 104 is inserted, the oil amount control plate 104 in the gap between the cam surface 111 of the loading cam 101 and the cage 102 has its wave surface 104a facing the cam surface 111 side. The oil amount control plate 104 that is disposed and is in the gap between the cam surface 110 of the input side disk 2 and the cage 102 is disposed with its wave surface 104a facing the cam surface 110 side. Further, the other side surfaces of the oil amount control plates 104 and 104 are in contact with the respective side surfaces of the cage 102 with almost no gap.

In this way, by arranging the oil amount control plate 104, the clearance between the cage 102 and the cam surface 111 of the loading cam 101 and the clearance between the cage 102 and the cam surface 110 of the input side disk 2 are reduced. Most of the oil can be filled with the oil amount control plate 104, and the wave surface 104a formed on one side surface of the oil amount control plate 104 is substantially parallel to the cam surface 110 (111). The gap between 102 and the cam surface 110 (111) can be efficiently filled. In addition, since the oil amount control plate 104 can rotate relative to the cage 102, the oil amount control plate 104 can fill most of the gap.
Therefore, the oil supplied toward the cam roller 103 by the centrifugal force from the oil hole provided in the input shaft 1 effectively spreads around the cam roller 103 and the periphery thereof, and the cam surfaces 110 and 111 and the surface of the cam roller 103 are sufficiently provided. Can be lubricated with oil.
Further, since the outer peripheral portion of the oil amount control plate 104 is located also on the outer peripheral portion side of the gap between the cam surface 110 (111) and the cage 102, and covers most of the outer peripheral portion side gap, Increases oil supply efficiency.

Moreover, the weight increase of the press apparatus 100 can be suppressed by forming the oil amount control board 104 with resin.
Further, by forming the oil amount control plate 104 with an elastic material such as rubber, a gap between the input side disk 2 and the loading cam 101 during the torque load (the input side disk 2 and the cage 102) And the increase or decrease of the clearance between the loading cam 101 and the cage 102. That is, when the gap between the input side disk 2 and the loading cam 101 is the narrowest, the oil amount control plate 104 is clamped in a state of being elastically compressed by the cam surface 110 (111) and the cage 102. If the gap is widened, the oil amount control plate 104 increases in thickness following the gap. Therefore, the gap can be increased or decreased.

  In addition, the oil amount control plate 104 can be formed between the cam surface 111 of the loading cam 101 and the cage 102 and between the cam surface 110 of the input side disk 2 and the cage 102 without using parts such as screws. Since they are respectively inserted in the gaps between them, an increase in weight of the pressing device 100, assembly costs, and the like can be suppressed.

In the present embodiment, the oil amount control plate 104 is formed separately from the cage 102, but may be formed integrally with the cage 102.
In this embodiment, the case where the input side disk 2 is pressed by the pressing device 100 has been described as an example. However, in the toroidal continuously variable transmission, the input / output relationship between the input side disk and the output side disk is reversed. In some cases. Therefore, the present invention can be applied to the case where the output side disk is pressed by the pressing device 100.

  Furthermore, in the present embodiment, the case where the present invention is applied to a double-cavity half-toroidal continuously variable transmission is described as an example. However, the present invention is not limited to this, and the present invention is not limited to this. It can also be applied to single-cavity half-toroidal and full-toroidal toroidal continuously variable transmissions.

2 Input disk (first disk)
3 Output disk (second disk)
11 Power roller 100 Press device 101 Loading cam 102 Cage 103 Cam roller 104 Oil amount control plates 110 and 111 Cam surface

Claims (1)

A first disk and a second disk that are concentrically and rotatably provided with their inner surfaces facing each other, a power roller that is sandwiched between the two disks, and the two disks that are A pressing device that presses in the approaching direction, and the pressing device is held between the loading cam and the cam surface of the loading cam and the cam surface of the first disk so as to be rollable by a cage. In a toroidal continuously variable transmission having
An oil amount control plate is provided in a gap between at least one of the cam surface of the loading cam and the cam surface of the first disk and the cage. Step transmission.

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