JP2015121298A - Toroidal type stepless change gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type stepless change gear capable of synchronizing axial movements of trunnion shafts of trunnions arranged in different cavities with each other and also suppressing a shift in position of one of the trunnions from affecting the position of the other trunnion.SOLUTION: A link mechanism 20 which couples trunnions to each other includes a link part 24 which couples a first trunnion holding a first roller arranged in one cavity and a second trunnion holding a second roller moving in the same direction with the first roller in an axial direction of a trunnion shaft, and arranged in the other cavity together so that the trunnions are moved in the same axial directions of trunnion shafts. The link part 24 has a shift absorbing mechanism which allows the first trunnion and second trunnion to shift in relative position in the axial directions of the trunnion shafts.

Description

  The present invention relates to a toroidal continuously variable transmission configured to sandwich a roller held by a trunnion between an input disk and an output disk and transmit torque from the input disk to the output disk via the roller. It is.

  The toroidal-type continuously variable transmission is configured such that a power roller is sandwiched between an input disk and an output disk whose surfaces facing each other are toroidal surfaces, and the power roller is tilted to cause a shift. . The power roller is held by a trunnion that moves back and forth in the axial direction of the trunnion shaft and rotates about the axis, and an actuator that moves the trunnion back and forth in the axial direction is provided for each trunnion. The actuator is connected to be rotatable about a central axis. In a half-toroidal continuously variable transmission, the distance between the toroidal surfaces gradually increases on the outer circumference side of the disk, and the power roller is directed toward the outer circumference side of the disk by the load caused by each disk pinching the power roller. Force to push out. Each trunnion is connected by a link to hold the power roller between each disk (ie, inside the cavity) against that force.

  Patent Documents 1 and 2 describe a so-called double cavity type toroidal continuously variable transmission having two pairs of disks. The cavities are arranged side by side on the same axis, and one disk (for example, output disk) in each cavity is disposed back to back, and the other disk (for example, input disk) faces the one disk. Thus, it arrange | positions at the both-ends part side in an axial direction, and a pair of power roller is arrange | positioned between each disk for every cavity. The power roller for each cavity is held by a trunnion as described above, and the trunnions are connected by a link. Similarly, the trunnion in one cavity and the trunnion in the other cavity are connected. As a member for connecting the trunnions across the cavities as described above, Patent Document 1 describes a link having the same configuration as a link for connecting the trunnions in the cavities. In Patent Document 2, a link in one cavity is integrally formed with a connecting portion extending from the link toward the other cavity, and the link in the other cavity is connected to the connecting portion by a fastening member such as a bolt. The fastened configuration is described.

JP-A-11-294550 JP 2000-230622 A

  The configuration described in Patent Document 1 is a configuration in which four links are assembled in a rectangular shape or a cross beam shape, and a trunnion shaft is connected to an intersection of each link via a bearing. Therefore, the trunnions in each respective cavity can move relative to each other in opposite directions (opposite directions in the direction of the axis of the trunnion axis), as well as the trunnions of different cavities that are adjacent to each other. It can move relatively in the axial direction of the shaft. Since these trunnions and the power rollers held by the trunnions need to perform the same speed change operation in the respective cavities, it is necessary to move in the axial direction in synchronism. In the configuration, on the other hand, the trunnions adjacent to each other and the power rollers held by the trunnions perform different operations, and as a result, the power transmission efficiency as a whole of the double cavity type toroidal continuously variable transmission is reduced. The maximum traction coefficient may deteriorate.

  On the other hand, the structure described in Patent Document 2 is a link that has been formed in the shape of a rectangular frame in the past and is made into two parts in consideration of the assembling property. In the state where the links are connected, a rectangular frame-shaped link is formed. That is, the above-described connecting portion that connects the trunnions across the cavities eventually functions in the same manner as the link that connects the trunnions in each cavity. Therefore, the movement of these trunnions in the axial direction can be synchronized, but on the other hand, if any one of the trunnions is misaligned, the connecting portion will cause the other trunnion to deviate similarly to the misalignment. It works to make it happen. In other words, the connecting part will synchronize even if the trunnions connected by the connecting part are synchronized, and since there is no function to correct such a deviation, in the end, the double cavity type toroidal stepless There is a possibility that the power transmission efficiency and the maximum traction coefficient of the transmission as a whole deteriorate.

  The present invention has been made by paying attention to the above technical problem, and synchronizes the movement of trunnions arranged in different cavities with respect to the axial direction of the trunnion shaft, and also trunnions of one of the trunnions. An object of the present invention is to provide a toroidal continuously variable transmission that can suppress the displacement of the position of the other from affecting the position of the other trunnion. .

  In order to achieve the above object, the invention of claim 1 has two cavities formed by a pair of disks, the surfaces of the pair of disks facing each other in the rotation center axis direction are formed on a toroidal surface, and Two rollers that are sandwiched between the disks and transmit torque between the disks are rotatably held by the trunnions, and the trunnion shafts provided in the trunnions are connected by a link mechanism. In the toroidal continuously variable transmission, the link mechanism prevents the trunnions holding the rollers provided in the cavities from moving in the direction of exiting the cavities and relatively moves in the axial direction of the trunnion shaft. A first link portion connected to each other and a first row disposed in one cavity A first trunnion that holds the second trunnion that holds the second roller disposed in the other cavity that moves in the same direction as the first roller in the axial direction of the trunnion shaft in the axial direction of the trunnion shaft A second link portion that is coupled so as to move in the same direction, and the second link portion allows a displacement of a relative position of the first trunnion and the second trunnion in the axial direction of the trunnion shaft. It has an absorption mechanism.

  According to a second aspect of the present invention, in the first aspect of the invention, the displacement absorbing mechanism is constituted by an elastically deformable portion provided in at least a part of the second link portion. It is a transmission.

  According to a third aspect of the present invention, in the first aspect of the invention, the deviation absorbing mechanism is formed by a gap provided between at least one trunnion of the first trunnion and the second trunnion and the second link portion. It is a toroidal continuously variable transmission characterized by being comprised.

  The invention of claim 4 is the invention according to any one of claims 1 to 3, wherein in the first link portion, the trunnions connected by the first link portion move to the opposite side in the axial direction of the trunnion shaft. The toroidal continuously variable transmission is characterized in that the trunnion can swing between the trunnions and is held while being restricted from moving in the axial direction of the trunnion shaft.

  According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the second link portion is configured to hold the first trunnion and the second trunnion rotatably. This is a toroidal continuously variable transmission.

  According to this invention, the trunnions holding the rollers provided in one of the cavities are connected to each other so as to move relatively in the axial direction of the trunnion shaft by the first link portion. Further, the first trunnion holding the first roller disposed in one cavity and the second trunnion holding the second roller disposed in the other cavity are the same in the axial direction of the trunnion shaft by the second link portion. Connected to move in the direction. Therefore, the trunnion connected to the first link portion and the trunnion connected to the second link portion can move in the axial direction of the trunnion shaft in synchronization. Further, the second link portion has a displacement absorbing mechanism that allows displacement of the relative positions of the first trunnion and the second trunnion in the axial direction of the trunnion shaft. Therefore, even when one of the first trunnion and the second trunnion is displaced in the axial direction of the trunnion shaft, the displacement of the trunnion is prevented from affecting the position of the other trunnion. can do.

It is a front view for demonstrating the structure of the upper link provided in the toroidal type continuously variable transmission which concerns on this invention. It is sectional drawing which follows the II-II line in FIG. It is a front view for demonstrating the other structure of an upper link. It is sectional drawing which follows the IV-IV line in FIG. It is sectional drawing for demonstrating an example of a structure of the toroidal type continuously variable transmission made into the object of this invention. It is sectional drawing which follows the VI-VI line in FIG.

  A toroidal-type continuously variable transmission according to the present invention includes a trunnion that rotatably holds a power roller sandwiched between an input disk and an output disk, and is characterized by links that connect the trunnions. A disk, a power roller, a trunnion, a thrust generation mechanism that presses each disk, a control device for shifting, and the like are configured in the same manner as those used in a conventionally known toroidal continuously variable transmission. One example thereof is described in JP2012-237370A. The configuration will be briefly described with reference to FIGS. In the example shown in FIG. 5, two input disks 2, 3 fitted so as to rotate integrally with the rotating shaft 1, and disposed between the input disks 2, 3 and relatively rotatable with the rotating shaft 1. Are provided with two output disks 4 and 5 fitted to the rotary shaft 1. Accordingly, the first input disk 2 fitted to one end of the rotating shaft 1 (the left end in FIG. 5) and the first output disk 4 arranged to face the first input disk 2 Thus, the first cavity 6 is formed. Similarly, a second input disk 3 fitted to the other end of the rotating shaft 1 (the right end in FIG. 5) and a second output disk 5 disposed opposite to the second input disk 3. Thus, the second cavity 7 is formed. That is, the toroidal continuously variable transmission shown in FIG. 5 is a double cavity type toroidal continuously variable transmission. In addition, between the surface opposite to the surface facing the first input disk 2 in the first output disk 4 and the surface opposite to the surface facing the second input disk 3 in the second output disk 5. Are arranged with the output gear 35 sandwiched therebetween.

  In addition, a surface where the first input disk 2 and the first output disk 4 face each other and a face where the second input disk 3 and the second output disk 5 face each other are formed on a toroidal surface, and the curvature of the toroidal surface is formed. The center is in the vicinity of the outer peripheral edge of each disk 2, 3, 4, 5 or outside thereof. That is, the toroidal continuously variable transmission shown in FIG. 5 is a half toroidal continuously variable transmission configured such that the distance between the toroidal surfaces gradually increases on the outer peripheral side of the disk. Further, two power rollers 8 and 9 are sandwiched between the first input disk 2 and the first output disk 4, and two power rollers are provided between the second input disk 3 and the second output disk 5. 10 and 11 are sandwiched.

  The toroidal type continuously variable transmission configured as described above transmits torque by the shearing force of oil interposed between the disk and the power roller. A thrust generating mechanism 12 for pressing is provided. In the example shown in FIG. 5, a thrust generating mechanism configured to press each of the disks 2, 3, 4, 5 based on the hydraulic pressure supplied to the hydraulic cylinder 13 is shown, but a cam mechanism, a screw mechanism, etc. Thrust can also be generated by other mechanisms.

  In the configuration in which the power rollers 8, 9 (10, 11) are sandwiched between the pair of disks 2, 4 (3, 5), the radial direction of the rotary shaft 1 along the rotation center axis of the power rollers 8, 9, 10, 11 The power rollers 8, 9, 10, and 11 are pressed to the outside at. Therefore, the power rollers 8, 9, 10, 11 are suppressed from moving to the outer peripheral side in the radial direction of the rotating shaft 1. In this state, the power rollers 8, 9, 10, and 11 are rotatably held by trunnions 14, 15, 16, and 17 arranged in the vertical direction. Since the trunnions 14, 15, 16, and 17 that hold the power rollers 8, 9, 10, and 11 are substantially the same, the trunnions 14 and 15 that hold the power rollers 8 and 9 provided in the first cavity 6 are used. Only the configuration will be described.

  FIG. 6 is a cross-sectional view for explaining the configuration of the trunnions 14 and 15. As shown in FIG. 6, the trunnion 14 has a main body portion 14a formed so as to surround the upper and lower sides of the power roller 8 in the vertical direction and the outer peripheral side surface of the first cavity 6, and the vertical direction from the main body portion 14a in the vertical direction. The first trunnion shaft 14b is provided. Similarly, the second trunnion 15 protrudes upward and downward in the vertical direction from the main body 15a formed so as to surround the upper and lower sides of the power roller 9 in the vertical direction and the outer peripheral side surface of the first cavity 6. The second trunnion shaft 15b is provided. The trunnion shafts 14b and 15b are rotatably held by an upper link 20 and a lower link 21, which will be described later. Therefore, the trunnion shafts 14b and 15b prevent the power rollers 8 and 9 from being pressed outwardly in the radial direction of the rotating shaft 1 and coming out of the first cavity 6 as described above.

  The trunnions 14 and 15 have a function of shifting the power rollers 8 and 9 in the vertical direction in addition to the function of preventing the power rollers 8 and 9 from coming out of the first cavity 6 as described above. doing. Therefore, the hydraulic actuators 18 and 19 for moving the trunnions 14 and 15 up and down are connected to the lower ends of the trunnion shafts 14b and 15b. When the trunnions 14 and 15 are moved in the vertical direction by the hydraulic actuators 18 and 19, the tangential direction of the power rollers 8 and 9 at the portion where the power rollers 8 and 9 are in contact with the disks 2 and 4 and the respective disks 2. , 4 is different from the rotation direction. Therefore, side slip occurs in the power rollers 8 and 9, and the power rollers 8 and 9 and the trunnions 14 and 15 rotate around the central axes X1 and X2 of the trunnion shafts 14b and 15b. As a result, the distance from the position where the input disk 2 and the power rollers 8 and 9 are in contact to the central axis of the rotary shaft 1, and the position where the output disk 4 and the power rollers 8 and 9 are in contact are the central axis of the rotary shaft 1. The distance is changed and the speed is changed.

  When shifting in such a manner, one power roller provided in the first cavity 6 (hereinafter referred to as the first power roller 8) and the other power roller provided in the first cavity 6 (hereinafter referred to as the first power roller 8). The second power roller 9 is moved in the opposite direction in the vertical direction (the same direction in the rotation direction of the disks 2, 3, 4 and 5). Similarly, one power roller provided in the second cavity 7 (hereinafter referred to as a third power roller 10) and the other power roller provided in the second cavity 7 (hereinafter referred to as a fourth power roller 11). ) Are moved in the opposite direction in the vertical direction. Further, the third power roller 10 provided on the opposite side of the first power roller 8 across the output gear 35 is moved in the same direction as the first power roller 8 in the vertical direction, and similarly sandwiches the output gear 35. The fourth power roller 11 provided on the side opposite to the second power roller 9 is moved in the same direction as the second power roller 9 in the vertical direction. Further, after shifting, the trunnions 14 and 15 moved in the vertical direction are returned to the original positions. In other words, the trunnions 14 and 15 are moved to positions where the tangential direction of the power rollers 8 and 9 and the rotational direction of the disks 2 and 4 coincide with each other at the contact portion between the power rollers 8 and 9 and the disks 2 and 4. . In the following description, the position is expressed as a neutral point.

  As described above, the power rollers 8 and 9 are pressed by the disks 2 and 4 and receive a load directed outward in the radial direction of the rotary shaft 1. When the transmission gear ratio is “1”, the rotation center axes of the first power roller 8 and the second power roller 9 coincide with each other on the same straight line. Therefore, when the discs 2 and 4 sandwich the power rollers 8 and 9 as described above, the load is applied in a direction in which the first power roller 8 and the second power roller 9 are separated from each other in the rotation center axis direction. Receive. Similarly, the third power roller 10 and the fourth power roller 11 receive a load in a direction away from each other in the rotation center axis direction.

  On the other hand, when the gear ratio is other than “1”, the rotation center axis of the first power roller 8 and the rotation axis of the second power roller 9 are tilted. Similarly, tilting is performed so that the rotation center axis of the third power roller 10 and the rotation center axis of the fourth power roller 11 intersect. Therefore, as described above, when the first power roller 8 and the second power roller 9 receive a load from the first input disk 2 and the first output disk 4, the first power roller 8 and the second power roller 9 are A load component in a direction away from each other in the rotation center axis direction and a load component in a direction parallel to the center axis line of the rotation shaft 1 are generated. Similarly, when the third power roller 10 and the fourth power roller 11 receive a load from the second input disk 3 and the second output disk 5, the third power roller 10 and the fourth power roller 11 are rotated with respect to the rotation center axis. A load component in a direction separated from each other in the direction and a load component in a direction parallel to the central axis of the rotation shaft 1 are generated. The load component in the direction parallel to the central axis of the rotary shaft 1 is the same direction for the first power roller 8 and the second power roller 9, and similarly, the third power roller 10 and the fourth power roller 11 are the same direction. It becomes. Further, the direction of the load received by the first power roller 8 and the second power roller 9 is opposite to the direction of the load received by the third power roller 10 and the fourth power roller 11.

  Therefore, the toroidal continuously variable transmission according to the present invention connects the above trunnions 14, 15, 16, and 17 and applies loads acting on the power rollers 8, 9, 10, and 11 as compressive stress or tensile stress. An upper link 20 and a lower link 21 are provided for handling. Since the upper link 20 and the lower link 21 can have the same configuration, in the following description, the upper link 20 will be described as an example. The upper link 20 and the lower link 21 correspond to the link mechanism in the present invention. FIG. 1 shows an example of the configuration of the upper link 20. The upper link 20 shown in FIG. 1 includes a first link member 22 that connects the first trunnion 14 that holds the first power roller 8, and the second trunnion 15 that holds the second power roller 9, and a third power roller. The second link member 23 that connects the third trunnion 16 that holds 10 and the fourth trunnion 17 that holds the fourth power roller 11, and the third link member that connects the first trunnion 14 and the third trunnion 16 24, and a fourth link member 25 that connects the second trunnion 15 and the fourth trunnion 17. The first link member 22 and the second link member 23 correspond to the first link portion in the present invention, and the third link member 24 and the fourth link member 25 correspond to the second link portion in the present invention.

  Further, the third link member 24 and the fourth link member 25 are configured to be able to bend and deform in the thickness direction. Specifically, it is formed of a material having a relatively low rigidity (Young's modulus), or is formed so that the cross-sectional second moment of the central portion in the longitudinal direction of each link member 24, 25 is relatively small. The first link member 22 and the second link member 23 are made of a material having rigidity higher than that of the third link member 24 and the fourth link member 25 so as not to bend and deform in the thickness direction. The cross-sectional secondary moment is formed larger than that of the third link member 24 and the fourth link member 25.

  The trunnions 14, 15, 16, and 17 are fitted to the link members 22, 23, 24, and 25 described above. More specifically, the trunnion shafts 14b, 15b, 16b, and 17b of the trunnions 14, 15, 16, and 17 are fitted. A cross-sectional view for explaining an example of the configuration is shown in FIG. In the example shown in FIG. 2, a state in which the first link member 22 and the third link member 23 are fitted is shown. Since other link members can be configured in the same manner, the following description will be given by taking as an example a state in which the first link member 22 and the third link member 23 are fitted. In the example shown in FIG. 2, a first through hole 26 penetrating in the thickness direction is formed at one end of the first link member 22. In addition, a cylindrical portion 27 protruding to the lower surface side is formed at one end portion of the third link member 24, and a second through hole 28 is formed on the same axis as the cylindrical portion 27. Since the cylindrical portion 27 and the second through hole 28 are configured so that the upper end portion of the first trunnion shaft 14b is inserted, the radius thereof is formed to be greater than the radius of the upper end portion of the first trunnion shaft 14b. ing. As described above, since the first trunnion 14 rotates around the central axis of the first trunnion shaft 14b, the needle bearing 29 is provided between the cylindrical portion 27 and the first trunnion shaft 14b. .

  On the other hand, the first link member 22 is formed with a third through hole 30 penetrating in the width direction at an intermediate portion in the longitudinal direction, and a pin connected to a fixing portion such as a case (not shown) is connected to the third through hole 30. Has been inserted. That is, the first link member 22 is configured to be able to swing around the third through hole 30. Similarly, the second link member 23 is swingably held by a pin (not shown). Therefore, the major axis of the first link member 22 and the central axis of the first trunnion shaft 14b may be inclined. Therefore, a cylindrical member 31 whose outer peripheral surface has a circular arc shape is fitted to the outside of the cylindrical portion 27. That is, even when the first link member 14 is inclined such that the long axis of the first link member 14 is inclined with respect to the central axis of the first trunnion shaft 14b, the inner wall surface of the first through hole 26 and the cylinder are always provided. It is comprised so that the outer peripheral surface of the member 31 may contact.

  A first washer 32 is provided in the vertical gap between the lower end surface of the cylindrical portion 27 and the cylindrical member 31 and the first trunnion 14, and a second washer 33 is provided on the upper surface of the third link member 24. Then, a fixing member 34 such as a snap ring is engaged with the upper end portion of the first trunnion shaft 14b in the axial direction so as to restrict the movement of the second washer 33 in contact with the upper surface of the second washer 33. Is provided. That is, the first trunnion 14 is integrated with the third link member 24 in the vertical direction.

  Next, the operation of the upper link 20 configured as described above will be described. As described above, the load that separates the first power roller 8 and the second power roller 9 toward the outer side in the radial direction of the rotating shaft 1 along the rotation center axis acts on the first link member 22. The load acting on the first link 22 acts against the longitudinal direction of the first link member 22. Therefore, the first link member 22 is responsible for the load as a tensile stress. Similarly, a load that separates the third power roller 10 and the fourth power roller 11 toward the outer side in the radial direction of the rotating shaft 1 along the rotation center axis acts on the second link member 23. Therefore, the second link member 23 is responsible for the load as a tensile stress. Further, the load received by the first power roller 8 and the second power roller 9 in a direction parallel to the central axis of the rotary shaft 1 and the third power roller 10 and the fourth power roller 11 are parallel to the central axis of the rotary shaft 1. The load received in any direction acts on the third link member 24 and the fourth link member 25. Similarly, the loads acting on the third link member 24 and the fourth link member 25 act against the longitudinal directions of the third link member 24 and the fourth link member 25, respectively. The load acting on the third link member 24 and the fourth link member 25 differs in the compression direction and the pulling direction depending on the transmission ratio. Therefore, the third link member 24 and the fourth link member 25 are responsible for the load as compressive stress or tensile stress.

  Further, as described above, each link member 22, 23, 24, 25 receives a load from each trunnion shaft 14 b, 15 b, 16 b, 17 b, so that the inner wall surface of the first through hole 26 and the outer peripheral surface of the cylindrical member 31 There is a friction force. Therefore, when the second trunnion 15 moves up and down, the first link member 22 swings around the third through hole 30 and moves the first trunnion 14 up and down. As described above, the first trunnion 14 and the second trunnion 15 move in opposite directions in the vertical direction, and therefore the first trunnion 14 and the second trunnion 15 can move up and down in synchronization. . That is, the movement amount of the first trunnion 14 and the movement amount of the second trunnion 15 can be matched. Further, the first trunnion 14 and the third trunnion 16 are integrated in the vertical direction by the third link member 24. Therefore, when the first trunnion 14 moves up and down, the third trunnion 16 also moves up and down together. As described above, the first trunnion 14 and the third trunnion 16 move in the same direction in the vertical direction. Therefore, the first trunnion 15 and the third trunnion 16 can move up and down synchronously. . That is, the movement amounts of the first trunnion 15 and the third trunnion 16 can be matched.

  In a steady state where no speed change is made, the first trunnion 14 functions as a reaction force in order to transmit the torque transmitted from the first input disk 2 to the power roller 8 to the first output disk 4. Therefore, the hydraulic pressure of the hydraulic actuator 18 that moves the first trunnion 14 up and down is controlled so as to generate a thrust according to the transmitted torque. In other words, the vertical load acting on the first trunnion 14 based on the transmitted torque and the vertical load acting on the first trunnion 14 based on the hydraulic pressure of the hydraulic actuator 18 are balanced, thereby 1 trunnion 14 is maintained at a neutral point.

  On the other hand, as described above, since frictional force acts on the first trunnion shaft 14b and the first link member 22, the first trunnion 14 may be slightly shifted from the neutral point. Specifically, each component member usually has an inevitable error due to processing accuracy, assembly accuracy, and the like, and the positions of the first trunnion 14 and the third trunnion 16 may be different based on the error. On the other hand, as described above, the positions of the first trunnion 14 and the third trunnion are inevitable in processing or assembling as described above according to the frictional force generated in the first trunnion shaft 14b and the first link member 22. There is a possibility that the position will be shifted more than the difference in position based on the error. In the following description, as described above, the difference between the positions of the trunnions is more than the amount of the difference between the positions of the trunnions based on the processing accuracy and the assembly accuracy.

  When the first trunnion 14 is slightly shifted from the neutral point as described above, the third link member 24 is bent and deformed in the thickness direction. Therefore, it is possible to suppress the third trunnion 16 from moving up and down integrally with the first trunnion 14. Therefore, it can suppress that the position of the up-and-down direction of the 3rd power roller 10 hold | maintained at the 3rd trunnion 16 shifts | deviates, and it can suppress that the reaction force for transmitting torque falls. As a result, it is possible to prevent the third power roller 10 and the second input disk 3 and the second output disk 5 from slipping, so that the power transmission efficiency of the toroidal continuously variable transmission as a whole decreases or It can suppress that a maximum traction coefficient falls. In other words, it is possible to suppress the deviation of the position of any one trunnion from affecting the positions of other trunnions. In other words, any trunnion position shift can be allowed.

  Accordingly, the elastically deformed portions of the third link member 24 and the fourth link member 25 absorb the displacement of the trunnion position, and correspond to the displacement absorbing mechanism in the present invention. In addition, since the load which acts on the longitudinal direction of the 3rd link member 24 and the 4th link member 25 is comparatively small, even if it is a case where it forms with a material with low rigidity as mentioned above, the 1st trunnion 14 and the 3rd There is no displacement so that the trunnion 16 is separated or the second trunnion 15 and the fourth trunnion 17 are separated.

  As described above, when the third link member 24 or the fourth link member 25 is elastically deformed to allow any trunnion position shift, the third link is corrected so that the trunnion whose position is shifted is corrected. Elastic force can be applied by the member 24 or the fourth link member 25.

  In the above description, the example in which the third link member 24 is disposed in contact with the upper surface of the first link member 22 has been described. However, as illustrated in FIGS. The three link members 24 may be arranged in contact with each other. Specifically, the cylindrical portion 27 may be formed on the upper surface side of the third link member 24, and the washer 33 may be disposed on the upper end surface of the cylindrical portion 27.

  In addition, the toroidal continuously variable transmission according to the present invention is basically configured such that the trunnions provided in the two cavities are connected to each other by the link member and moved in the same direction in the axial direction of the trunnion shaft. It suffices if the relative position shift between the trunnions can be allowed in the axial direction. Therefore, it is not limited to elastically deforming as described above, and a predetermined gap may be provided between the trunnion body and the link member. Specifically, a gap may be formed between at least one of the trunnions held by the link member and the link member. The predetermined gap here is a gap larger than an error caused by errors such as machining accuracy and assembly accuracy, for example, based on a deviation amount allowed between trunnions held by one link member. Can be determined.

  When the trunnions connected by the link member are relatively displaced in the axial direction of the trunnion shaft by forming the gap as described above, first, the trunnion moves so as to close the gap, and then, A load can be applied to a trunnion whose position is shifted so that each trunnion moves integrally. As a result, the relative position between the trunnions in the axial direction of the trunnion shaft can be allowed, and a load can be applied to synchronize the trunnions. The gap between the trunnion and the link member corresponds to the deviation absorbing mechanism in the present invention.

  In addition, the link mechanism in this invention may be configured by combining a plurality of members, or may be formed integrally.

  2,3 ... Input disk 4,5 ... Output disk 6,7 ... Cavity 8,9,10,11 ... Power roller 14,15,16,17 ... Trunnion, 14b, 15b, 16b, 17b ... Trunnion Shaft, 20 ... upper link, 21 ... lower link, 22, 23, 24, 25 ... link member.

Claims (5)

A pair of disks facing each other in the rotational center axis direction are formed on a toroidal surface and have two cavities formed by the pair of disks, and are sandwiched between the disks to generate torque between the disks. In the toroidal continuously variable transmission in which the two rollers that transmit are rotatably held by the trunnions, and the trunnion shafts provided in the trunnions are connected by a link mechanism.
The link mechanism is configured to connect the trunnions holding the rollers provided in the cavities so that the trunnions are prevented from moving in the direction of coming out of the cavities and relatively moved in the axial direction of the trunnion shaft. A first trunnion that holds the first roller disposed in one cavity, and a second roller that is disposed in the other cavity that moves in the same direction as the first roller in the axial direction of the trunnion shaft. A second link portion for connecting the second trunnion so as to move in the same direction in the axial direction of the trunnion shaft;
The second link portion includes a displacement absorbing mechanism that allows a displacement of a relative position between the first trunnion and the second trunnion in the axial direction of the trunnion shaft. Machine.   2. The toroidal continuously variable transmission according to claim 1, wherein the deviation absorbing mechanism is configured by an elastic deformation portion provided in at least a part of the second link portion.   The said shift | offset | difference absorption mechanism is comprised by the clearance gap provided between the at least one trunnion of the said 1st trunnion and the said 2nd trunnion, and the said 2nd link part. Toroidal continuously variable transmission.   The first link part is swingable between the trunnions so that the trunnions connected by the first link part can move to the opposite side in the axial direction of the trunnion shaft, and the trunnion 4. The toroidal continuously variable transmission according to claim 1, wherein movement of the shaft in the axial direction is restricted and held.   5. The toroidal type non-rotating device according to claim 1, wherein the second link portion is configured to rotatably hold the first trunnion and the second trunnion, respectively. Step transmission.

Images