JP2005054980A - Toroidal-type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a metal piece from getting mixed in lubricating oil flowing through the interiors of lubricating oil passages 27a, 27b and align the center axis of the pivot 9a with the center axis of the rod 17 with good accuracy in a structure where a pivot 8a mounted at the end part of a trunnion 7 and a rod 17 attached to an actuator 10 are connected by screwing. <P>SOLUTION: In a circular hole 33 opened in the tip surface of the pivot 9a, a female screw part 32 is formed rather closer to the opening and an inside diameter side cylindrical surface part 36 is formed on the inner side thereof. A male screw part 31 formed rather closer to the tip of the intermediate part of the rod 17 is engaged with the female screw part 32, and an outside diameter side cylindrical surface part 37 formed at the tip part of the rod 17 is forced into the inside diameter side cylindrical surface part 36. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an improvement of a toroidal type continuously variable transmission used as an automatic transmission for an automobile, and has a structure in which a trunnion that rotatably supports a power roller and a rod of an actuator for shifting can be connected later. The invention was invented to ensure durability and reliability.

  The use of a half-toroidal toroidal continuously variable transmission as shown in FIGS. 15 to 17 has been studied and partially implemented as an automatic transmission for automobiles. This toroidal type continuously variable transmission is called a double cavity type, and supports input-side disks 2 and 2 around both ends of the input shaft 1 via ball splines 3 and 3. Therefore, both the input side disks 2 and 2 are supported concentrically and freely in a synchronized manner. An output gear 4 is supported around the intermediate portion of the input shaft 1 so as to be freely rotatable relative to the input shaft 1. The output side disks 5 and 5 are respectively spline-engaged with both ends of a cylindrical portion provided at the center of the output gear 4. Accordingly, both the output side disks 5 and 5 rotate in synchronism with the output gear 4.

  A plurality (usually 2 to 3) of power rollers 6 and 6 are sandwiched between the input disks 2 and 2 and the output disks 5 and 5, respectively. Each of these power rollers 6 and 6 is rotatably supported by inner surfaces of trunnions 7 and 7 via support shafts 8 and 8 and a plurality of rolling bearings, respectively. The trunnions 7, 7 are pivots 9a, 9b provided concentrically with each other for each trunnion 7, 7 at both ends in the length direction (vertical direction in FIGS. 15 and 17, front and back direction in FIG. 16). Oscillating and displacing around the center. The operation of inclining the trunnions 7 and 7 is performed by displacing the trunnions 7 and 7 in the axial direction of the pivots 9a and 9b by the hydraulic actuators 10 and 10. The inclination angle of 7 is synchronized with each other hydraulically and mechanically.

  That is, when changing the inclination angle of the trunnions 7 and 7 in order to change the transmission ratio between the input shaft 1 and the output gear 4, the trunnions 7 and 7 are moved by the actuators 10 and 10. For example, the right power roller 6 on the right side of FIG. 17 is on the lower side of the figure and the left side of the power roller 6 is on the upper side of the figure in opposite directions (same direction with respect to the rotation direction of the disks 2 and 5) Respectively. As a result, the direction of the tangential force acting on the contact portion between the peripheral surface of each of the power rollers 6 and 6 and the inner surface of each of the input side disks 2 and 2 and the output side disks 5 and 5 changes. (Side slip occurs at the contact portion). The trunnions 7 and 7 swing (tilt) in opposite directions around the pivots 9a and 9b pivotally supported by the support plates 11 and 11 in accordance with the change in the direction of the force. As a result, the contact position between the peripheral surface of each of the power rollers 6 and 6 and the inner surface of each of the input and output disks 2 and 5 changes, and rotation between the input shaft 1 and the output gear 4 occurs. The gear ratio changes.

  Regardless of the number of these actuators 10, 10, the supply / discharge state of the pressure oil to each of the actuators 10, 10 is performed by one control valve 12, and any one trunnion 7 is moved. I'm trying to provide feedback. This control valve 12 is fitted in a sleeve 14 that is displaced in the axial direction (front and back direction in FIG. 15, left and right direction in FIG. 17) by a stepping motor 13, and axially displaceable on the inner diameter side of this sleeve 14. And a spool 15. The trunnions 7 and 7 are connected to the pistons 16 and 16 of the actuators 10 and 10. The rods 17 and 17 are used to transmit the movements of the pistons 16 and 16 to the trunnions 7 and 7, respectively. Among them, a recess cam 18 is fixed to an end of a rod 17 attached to any one trunnion 7. A feedback mechanism is configured to transmit the movement of the rod 17, that is, the combined value of the displacement amount in the axial direction and the displacement amount in the rotation direction, to the spool 15 via the recess cam 18 and the link arm 19. doing. Moreover, the synchronous cable 20 is spanned between a pair of trunnions 7 and 7 installed in the same cavity part (between the input side disk 2 and the output side disk 5 facing each other), The inclination angles of these trunnions 7, 7 are mechanically synchronized. A synchronization cable (not shown) is also routed between the trunnions 7, 7 installed in different cavities.

  When switching the speed change state, the stepping motor 13 displaces the sleeve 14 to a predetermined position corresponding to the speed ratio to be obtained, and opens the flow path of the control valve 12 in a predetermined direction. As a result, pressure oil is sent to the actuators 10 and 10 in a predetermined direction, and the actuators 10 and 10 displace the trunnions 7 and 7 in a predetermined direction. That is, the trunnions 7 and 7 swing around the pivots 9a and 9b while being displaced in the axial direction of the pivots 9a and 9b as the pressure oil is fed. Then, the movement (axial direction and swing displacement) of any one of the trunnions 7 is transmitted to the spool 15 via a recess cam 18 and a link arm 19 fixed to the end of the rod 17, and this spool 15 is displaced in the axial direction. As a result, in the state where the trunnion 7 is displaced by a predetermined amount, the flow path of the control valve 12 is closed, and the supply and discharge of the pressure oil to the actuators 10 and 10 are stopped.

  During operation of the toroidal type continuously variable transmission as described above, one input side disk 2 (left side in FIGS. 15 and 16) is connected to a loading cam type as shown by a drive shaft 21 connected to a power source such as an engine. Alternatively, it is rotationally driven via a hydraulic pressing device 22. As a result, the pair of input side disks 2 and 2 supported at both ends of the input shaft 1 rotate synchronously while being pressed toward each other. Then, the rotation is transmitted to the output side disks 5 and 5 through the power rollers 6 and 6 and is taken out from the output gear 4.

  When the rotational speed of the input shaft 1 and the output gear 4 is changed, and when the deceleration is first performed between the input shaft 1 and the output gear 4, the trunnions 7 and 7 are moved by the actuators 10 and 10, respectively. The trunnions 9 and 9b are moved in the axial direction to swing the trunnions 7 and 7. The peripheral surfaces of the power rollers 6 and 6 are brought into contact with the central portion of the inner surface of the input side disks 2 and 2 and the outer peripheral portion of the inner surface of the output disks 5 and 5, respectively. Let On the other hand, when increasing the speed, the trunnions 7 and 7 are swung in the reverse direction, and the peripheral surfaces of the power rollers 6 and 6 are set to the outer periphery of the inner surfaces of the input disks 2 and 2. The trunnions 7 and 7 are inclined so as to come into contact with the portions closer to the center of the inner side surfaces of the output side disks 5 and 5 respectively. If the inclination angles of the trunnions 7 and 7 are set in the middle, the intermediate speed ratio (speed ratio) between the input shaft 1 and the output gear 4 including the constant speed transmission state as shown in FIG. can get.

  In the toroidal type continuously variable transmission constructed and operated as described above, the structure of the portion for transmitting the movement of the actuators 10 and 10 to the trunnions 7 and 7 is described in Patent Document 1 or Patent Document 2. It is described or implemented in many publications and is widely known. FIG. 18 shows a conventional structure. In the case of this conventional structure, the tip half (upper half) of the rod 17 is press-fitted into the support hole 23 formed at the center of the pivot 9a provided at one end (lower end) of the trunnion 7, and the pin 24 To prevent it from coming off. Further, a cylindrical portion 25 provided at the center portion of the piston 16 is fitted to the base half portion (lower half portion) of the rod 17 without rattling, and is screwed to the tip end portion (lower end portion) of the rod 17. The cylindrical portion 25 is fixed to the rod 17 and the trunnion 7 by the nut 26.

  A recess cam 18 (see FIG. 17) is externally fixed to the tip of the rod 17 as necessary. Lubricating oil passages 27a and 27b are provided in the central portion of the rod 17 and the inside of the trunnion 7, respectively, and the lubricating oil is fed into the rotation support portion of the power roller 6 provided on the inner surface of the trunnion 7. It is free. For this purpose, the downstream end of the lubricating oil passage 27a provided at the center of the rod 17 and the upstream end of the lubricating oil passage 27b provided inside the trunnion 7 are communicated with each other. During operation of the toroidal continuously variable transmission, lubricating oil (traction oil) is fed into a lubricating oil passage 27a provided at the center of the rod 17.

  In the case of the structure shown in FIG. 18 as described above, the connecting operation between the trunnions 7 and the rods 17 requires the press-in operation of the pins 24, so that each trunnion 7 is connected to the support plate 11 (FIG. 15). , 17)) before support. On the other hand, the combination work of each trunnion and each actuator for reasons other than the structure of the toroidal type continuously variable transmission itself, such as the structure (body shape) on the vehicle side where the toroidal type continuously variable transmission is mounted, It may be necessary to carry out after each of these trunnions is supported on the support plate. In such a case, if a male screw is formed at the tip of the rod attached to each actuator and a screw hole is formed at the center of the pivot provided at the end of each trunnion, each trunnion is supported by the support plate. After the support, the combination work of each trunnion and each actuator can be performed.

  A structure that can be used in the above-described case and screwed to a trunnion attached to a trunnion is described in Patent Document 3 and is conventionally known. In the case of the structure described in Patent Document 3, a screw hole is formed at one end portion of the trunnion, and the one end portion is formed so as to penetrate in the axial direction of the pivot. However, no particular consideration is given to the alignment between the pivot and the rod. For this reason, when the structure described in Patent Document 3 is adopted as it is, the following problems may occur.

  First, by using the screw hole as a through hole, fine metal pieces are easily mixed into the lubricating oil. In other words, minute burrs generated along with the formation of the female thread portion on the inner peripheral surface of the screw hole are likely to remain on the inner peripheral surface of the screw hole. When the screw hole is a through hole, the burr separated from the inner peripheral surface with use comes out of the screw hole from the opposite side of the rod hole, and the lubrication is performed. There is a possibility of being mixed in the oil and further sent to each part of the toroidal type continuously variable transmission. In particular, in the case of a structure in which lubricating oil flows through the through hole, this possibility is increased. The metal pieces (burrs) mixed in the lubricating oil are rolling contact portions (traction portions) between the inner surfaces of the input and output discs 2 and 5 and the peripheral surfaces of the power rollers 6 and 6. If the rolling contact portions (see FIGS. 16 to 18) of the rolling bearings supporting the power rollers 6 and 6 are entered, the rolling contact portions are damaged. As a result, it may be difficult to ensure sufficient durability of the toroidal continuously variable transmission.

  Further, since the centering of the pivot and the rod is not particularly taken into consideration, there is a possibility that the shifting operation of the toroidal type continuously variable transmission becomes unstable. The reason for this is as follows. When the toroidal type continuously variable transmission is shifted, the rod rotates together with the pivot, and the piston 16 supported and fixed around the rod also rotates in the cylinder 28 (see FIG. 17). In order to smoothly perform this rotation and stabilize the speed change operation of the toroidal type continuously variable transmission (suppress the resistance against the swinging displacement of the trunnion 7 around the pivot shafts 9a and 9b), the piston 16 Is fixed around the rod 17 concentrically with the rod 17, and the rod 17 needs to be concentrically connected to the pivot 9 a provided at the end of the trunnion 7. The better the concentricity between these members 16, 17, 9a, the more stable the shifting operation of the toroidal continuously variable transmission.

  However, since there is a gap between the male screw portion and the female screw portion that are screwed together, when these male screw portion and female screw portion are screwed together, the central axis of the member provided with these male screw portions and the female screw portion It is difficult to match the central axis of the member provided with high accuracy. Even if they are matched, it is considered inevitable that the cost required to form the male screw portion and the female screw portion is very high.

Japanese Patent Laid-Open No. 7-243494 JP 11-153203 A JP 2003-148578 A

  In view of the circumstances as described above, the present invention realizes a structure in which a rod attached to an actuator and a trunnion are coupled by screwing so that a metal piece separated from a screw portion is not mixed in the lubricating oil. Invented as much as possible. In addition, if necessary, a structure in which the center axis of the rod and the center axis of the pivot provided at the end of the trunnion can be matched with high precision is realized, and the shifting operation of the toroidal continuously variable transmission is stable. It is intended to be made.

Each of the toroidal type continuously variable transmissions of the present invention is similar to the above-described conventionally known toroidal type continuously variable transmissions, and includes an input side disk and an output side disk, a plurality of power rollers, and a plurality of trunnions. And a plurality of actuators and a plurality of rods.
Of these, the input-side disk and the output-side disk are supported concentrically so as to be freely rotatable relative to each other.
The power rollers are sandwiched between the disks.
Further, each trunnion is freely swingable and displaceable around pivots provided concentrically with each other at both ends in a state where the respective power rollers are rotatably supported.
The actuators are for displacing the trunnions in the axial directions of the pivots.
The rods are for transmitting the movements of the actuators to the trunnions.
Each trunnion and each rod are coupled. Therefore, in the case of the toroidal-type continuously variable transmission according to claim 1, a male screw provided at the tip of each rod is provided with a female screw provided at the center of the pivot at one end of each trunnion. Screwed into the part.

In particular, in the toroidal-type continuously variable transmission according to claim 1, a bottomed circle provided at one end of each trunnion at the center of the pivot without passing through the end in the axial direction. The female thread portion is formed on the inner peripheral surface of the hole.
Further, in the toroidal type continuously variable transmission according to claim 7, a male screw part concentric with the pivot, which is provided at the center of the distal end surface of the pivot provided at one end of each trunnion, The rods and the trunnions are coupled to each other by screwing a screw hole formed in a state of opening to the front end surfaces of the rods into the center of the rods. Furthermore, the lubricating oil can be freely fed into the lubricating oil passages provided in the respective trunnions through concave grooves formed in the axial direction of the rods on the outer peripheral surfaces of the rods.

In the toroidal-type continuously variable transmission according to claim 1 configured as described above, a female screw portion for screwing a male screw portion provided at a tip portion of the rod is formed on the inner peripheral surface of the bottomed circular hole. Therefore, the metal piece separated from the male screw portion or the female screw portion does not come out of the circular hole.
Further, in the case of the toroidal type continuously variable transmission according to claim 7, a concave groove for feeding the lubricating oil into the lubricating oil passage provided in each trunnion is provided on the outer peripheral surface of each rod. Since it is formed in the axial direction, the lubricating oil does not circulate through the portion where the male screw portion and the screw hole are formed. Therefore, like the toroidal-type continuously variable transmission according to the first aspect, the metal piece separated from the inner peripheral surface of the male screw portion or the screw hole does not come out of the screw hole.
For this reason, in any structure, the rolling contact portion between the inner surface of both the input side and output side disks and the peripheral surface of each power roller and the respective rolling bearings supporting these power rollers by the metal piece. It is possible to prevent the rolling contact portion from being damaged and to sufficiently ensure the durability of the toroidal continuously variable transmission.

Preferably, when the toroidal continuously variable transmission according to claim 1 is implemented, the female screw portion is formed in a portion near the opening of the circular hole, and a part of the circular hole is provided on the back side portion of the female screw portion. A cylindrical surface portion on the inner diameter side that is smaller than the crest diameter of the female screw portion and concentric with the female screw portion is formed. On the other hand, an outer diameter-side cylindrical surface portion that is concentric with the male screw portion and is not loosely formed on the inner diameter-side cylindrical surface portion is formed in a part of the rod closer to the tip than the male screw portion.
If comprised in this way, the center axis | shaft of the pivot provided in the edge part of each trunnion and the center axis | shaft of the said rod will be made to correspond with high precision based on the fitting of these inner-diameter side and outer-diameter side cylindrical surface parts. I can do things. Moreover, since it is easy to form both the inner diameter side and the outer diameter side cylindrical surface portions with high accuracy, an increase in cost can be suppressed.

Further, when forming both the cylindrical surface portions, it is preferable to provide a lubricating oil passage for sending lubricating oil to the support portion of each power roller in each trunnion and each rod. Then, the lubricating oil passage provided in each trunnion and the lubricating oil passage provided in each rod are communicated with each other.
Thus, when providing each of these lubricating oil passages, preferably, the axial length of the outer diameter side cylindrical surface portion is made longer than the axial length of the female screw portion.
If comprised in this way, the said outer-diameter side cylindrical surface part will begin to fit into the said inner-diameter side cylindrical surface part before the said external thread part begins to screw-engage with the said internal thread part. For this reason, even if a metal piece falls off from any one of the screw parts based on the screwing of the female screw part and the male screw part, the metal piece does not enter the lubricating oil passages.

Preferably, each actuator is a hydraulic type in which a piston fitted in the cylinder is displaced in the axial direction by supplying and discharging hydraulic pressure into the cylinder, and a cylindrical portion is provided at the center of the piston. The rods are inserted through the cylindrical portion. Then, in a state where the male screw portion and the female screw portion are screwed together and further tightened, the cylindrical portion is attached to an outward flange-like flange portion provided at a base end portion of each rod and one end portion of each trunnion. It is clamped from both ends in the axial direction, directly or via a washer, with the end surface of the provided pivot. Further, the pivot and the cylindrical portion are engaged with each other while preventing relative rotation.
If comprised in this way, the pivot of each said trunnion and each said piston can be combined concentrically with each other in the state which prevented relative rotation. In addition, when the trunnion is pivoted and displaced about the pivot, the piston can be smoothly rotated in the cylinder, and the shifting operation of the toroidal continuously variable transmission can be stabilized. .
In order to engage the pivot and the cylindrical portion in a state where relative rotation is prevented, the end portions of the pivot and the cylindrical portion are fitted to each other with peripheral surfaces having a non-circular cross-sectional shape. Combine. As the non-circular cross-sectional shape, it is possible to adopt a shape having a straight line part in the circumferential direction, such as serration (including spline) or oval shape.

More preferably, in a state where the male screw portion and the female screw portion are screwed together and further tightened, the cylindrical portion and the rod are engaged in a state in which relative rotation is prevented.
If comprised in this way, the said trunnion and each said rod will be combined in the state from which relative rotation was blocked | prevented through the said cylindrical part, The loosening prevention of the screwing part of the said male thread part and the said female thread part Is planned.
In order to prevent relative rotation between the cylindrical portion and the rod, the male screw portion and the female screw portion are screwed together and further tightened, and then a part of the cylindrical portion is plastically deformed to deform the rod. A structure that engages with a part and disables relative rotation between the cylindrical portion and the rod is conceivable. Alternatively, in a state in which the washer is combined with the cylindrical portion so as not to rotate relative to the cylindrical portion, the male screw portion and the female screw portion are screwed together and further tightened, and then a part of the washer is plastically deformed, and the rod A structure in which the relative rotation between the washer and the rod is made impossible is also conceivable.

On the other hand, when the toroidal-type continuously variable transmission according to claim 7 is carried out, preferably, each male screw is provided in a portion surrounding the base end portion of each male screw portion at the front end surface of the pivot provided at one end portion of each trunnion. A positioning column part having an outer diameter larger than the outer diameter of the part is formed concentrically with the pivot. Then, by positioning the positioning cylindrical portion formed at the tip of each rod on the positioning column portion, the center of each rod and the center of the pivot provided at one end of each trunnion are matched.
If comprised in this way, the center axis | shaft of the pivot provided in the edge part of each said trunnion and the center axis | shaft of each said rod can be made to correspond with high precision. In addition, since it is easy to form the outer peripheral surface of the positioning column and the inner peripheral surface of the positioning cylinder with high accuracy, an increase in cost can be suppressed.

Preferably, each of the actuators is a hydraulic type in which a piston is fitted in a cylinder provided in the actuator body so as to be displaceable in the axial direction of a pivot provided at both ends of each trunnion. The rod is inserted into a cylindrical portion provided in the center of the piston, and the lubricating oil supply path provided in the actuator body and the rod are connected to each other by an oil passage hole that connects the inner and outer peripheral surfaces of the cylindrical portion. The groove formed on the outer peripheral surface is communicated.
If comprised in this way, lubricating oil can be efficiently sent in the lubricating oil channel | path provided in each said trunnion.

In this case, a washer is preferably sandwiched between the tip surface of the cylindrical portion provided at the center of the piston and the tip surface of the pivot provided at one end of each trunnion. The groove formed on the outer peripheral surface of each rod communicates with the lubricating oil passage provided inside each trunnion via a recess formed on the side surface of the washer facing the tip surface of the pivot. Let
If comprised in this way, it is the structure where the washer was pinched | interposed between the front end surface of the said cylindrical part, and the front end surface of the said pivot, and lubricating oil can be efficiently sent in the lubricating oil path provided in each said trunnion The structure can be realized.

More preferably, each of the rods is formed in a cylindrical shape, and a screw hole is formed on the inner peripheral surface of an inward flange-shaped flange portion formed near the tip of the inner peripheral surface of the rod. Then, a lock nut inserted into each rod is screwed into a portion of the male screw at the tip portion protruding from the flange portion to the side opposite to the pivot, and the lock nut is tightened toward one side surface of the flange portion. .
If comprised in this way, the loosening prevention of the said screw hole and the said external thread part can be aimed at reliably.

  FIGS. 1-2 has shown Example 1 of this invention corresponding to Claims 1-3. The feature of the present invention, including this embodiment, is the structure of the connecting portion between the pivot 9 a provided at one end of the trunnion 7 and the rod 17 attached to the actuator 10. The structure and operation of the other parts are the same as those of the conventional toroidal type continuously variable transmission including the structure shown in FIGS. 15 to 17 described above. Hereinafter, the characteristic part of the present invention and the part not described above will be mainly described. In addition, since the connecting portions of the plurality of trunnions and rods incorporated in the toroidal type continuously variable transmission have the same structure, the illustration and the following explanation are the same as the ends of one trunnion 7 and one This is done only for the joint with the end of the rod 17.

  The pivot shafts 9a and 9b provided concentrically with each other at both ends of the trunnion 7 which rotatably supports the power roller 6 on the inner surface are aligned in the support holes 29 and 29 provided in the pair of support plates 11 and 11, respectively. It supports by the radial needle bearings 30 and 30 which have a function. Therefore, the trunnion 7 is freely movable in the axial direction (vertical direction in FIGS. 1 and 2) of the pivots 9a and 9b and swinging and displacing around the pivots 9a and 9b. The trunnion 7 is driven by the hydraulic actuator 10 in the axial direction of the pivots 9a and 9b via the rod 17.

  For this purpose, the male screw portion 31 provided near the tip of the intermediate portion of the rod 17 is replaced with a female screw portion 32 provided at the central portion of the pivot 9a at one end portion of the trunnion 7 (lower end portion in FIGS. 1 and 2). The trunnion 7 and the rod 17 are coupled by screwing. For this purpose, a bottomed circular hole 33 is provided at the center of the pivot shaft 9a so as not to penetrate one end of the trunnion 7 in the axial direction. That is, the trunnion 7 protrudes toward the inner side surface (right side in FIGS. 1 and 2) of the support plate 34 at both ends of the support plate 34 for supporting the power roller 6. A pair of pivot walls 35 are formed. The pivots 9a and 9b are provided concentrically on the outer surfaces (side surfaces opposite to each other) of the pivot support walls 35 and 35, respectively. The circular hole 33 is formed so as to open only at the distal end surface (the lower end surface in FIGS. 1 and 2) of the pivot 9 a on the one end side and not open on the inner side surface of the pivot wall portion 35.

  The female screw portion 32 is formed in a portion near the opening of the inner peripheral surface of the circular hole 33. On the other hand, an inner diameter side cylindrical surface portion 36 is formed in a part of the circular hole 33 at the back side of the female screw portion 32. The inner diameter side cylindrical surface portion 36 has a smaller diameter than the crest diameter of the female screw portion 32 and is formed concentrically with the female screw portion 32. The inner end of the circular hole 33 remains in the shape of a pilot hole that is processed when the circular hole 33 is formed. On the other hand, an outer diameter side cylindrical surface portion 37 is formed at a portion protruding from the male screw portion 31 at the distal end portion of the rod 17. The outer diameter side cylindrical surface portion 37 is concentric with the male screw portion 31 and can be fitted inside the inner diameter side cylindrical surface portion 36 without rattling. For this reason, the outer diameter of the outer diameter side cylindrical surface portion 37 in the free state is the same as or slightly larger than the inner diameter of the inner diameter side cylindrical surface portion 36 in the free state. The inner diameter side cylindrical surface portion 36 and the outer diameter side cylindrical surface portion 37 are fitted with an interference fit in a state where the male screw portion 31 and the female screw portion 32 are screwed together and further tightened.

  On the other hand, the actuator 10 allows the piston 16 to move in the axial direction (vertical direction in FIGS. 1 and 2) in a cylinder 40 provided in a cylinder body 39 fixed in a housing 38 (see FIGS. 15 and 17). It is configured by oil-tight fitting. The actuator 10 axially displaces the piston 16 by pushing and pulling the rod 17 by supplying and discharging hydraulic pressure to and from a pair of hydraulic chambers 41 a and 41 b partitioned by the piston 16 in the cylinder 40. It is configured like this. In order to transmit the movement of the piston 16 to the rod 17, a cylindrical portion 42 is provided at the center of the piston 16, and the rod 17 is inserted through the cylindrical portion 42. Then, in a state where the male screw portion 31 and the female screw portion 32 are screwed together and further tightened, the cylindrical portion 42 is connected to an outward flange-like flange portion 43 provided at the proximal end portion of the rod 17 and the one end side. And the end surface of the pivot shaft 9a. In the case of the present embodiment, a washer 44 is sandwiched between the end surface of the pivot 9 a and the end surface of the cylindrical portion 42. Further, a hexagonal hole 45 is provided in the central portion of the base end surface (the lower end surface in FIGS. 1 and 2) of the rod 17, and the rod 17 is connected to the male screw portion 31 and the female screw portion 32 with a tool such as a hexagon wrench. It is possible to tighten and rotate with a sufficiently large torque required for tightening.

  Lubricating oil passages 27 a and 27 b are provided in the inside of the trunnion 7 and the central portion of the rod 17 so that lubricating oil can be supplied to the rotation support portion of the power roller 6. Of these, the downstream end of the lubricating oil passage 27 a provided at the center of the rod 17 is open to the tip surface (the upper end surface in FIGS. 1 and 2) of the rod 17. The upstream end of the lubricating oil passage 27a communicates with an oil supply port (not shown) provided in the cylinder body 39 through an oil passage hole 46 formed in the cylindrical portion 42. On the other hand, the upstream half of the lubricating oil passage 27 b provided inside the trunnion 7 is formed in the pivot wall 35 so as to cross the inner end of the circular hole 33. The downstream half of the lubricating oil passage 27b is formed in the support plate 34 in the axial direction of the pivot 9a. The upstream half and the downstream half of these lubricating oil passages 27b communicate with each other so that the downstream end communicates with a portion that requires lubricating oil, and an opening that becomes unnecessary after processing is formed by plugs 47 and 47. It is blocking.

  As described above, in the case of the present embodiment, the female screw portion 32 for screwing the male screw portion 31 provided at the tip portion of the rod 17 is formed on the inner peripheral surface of the bottomed circular hole 33. Further, between the threaded portion between the two screw portions 31 and 32 and the lubricating oil passages 27a and 27b, there are fitting portions between the inner diameter side, the outer diameter side, and the cylindrical surface portions 36 and 37. To do. Therefore, the metal piece separated from the male screw portion 31 or the female screw portion 32 does not go out of the circular hole 33 due to mixing in the lubricating oil flowing in the lubricating oil passages 27a and 27b. For this reason, this metal piece supports the rolling contact portions between the inner surfaces of the input and output disks 2 and 5 and the peripheral surfaces of the power rollers 6 and 6, and the power rollers 6 and 6. The rolling contact portion (see FIGS. 15 to 17) of the rolling bearing can be prevented from being damaged, and the durability of the toroidal continuously variable transmission can be sufficiently secured.

  In the case of the present embodiment, the center axis of the pivot 9 a provided at the end of the trunnion 7 and the rod 17 are connected based on the fitting of the cylindrical surfaces 36 and 37 on the inner and outer diameter sides. The center axis can be matched with high accuracy. Therefore, it is possible to realize a toroidal continuously variable transmission that can perform a shifting operation in a stable state. In this case, it is possible to easily form both the inner diameter side and outer diameter side cylindrical surface portions 36 and 37 with high precision, such as turning and honing. For this reason, an increase in cost required to stabilize the speed change operation can be suppressed.

3 to 5 show a second embodiment of the present invention corresponding to claims 1 to 6. In the case of this example, first, the axial length of the cylindrical surface portion 37 on the outer diameter side provided at the distal end portion of the rod 17 rather than the axial length L _{32 of} the female screw portion 32 formed near the opening of the circular hole 33. L ₃₇ is lengthened (L ₃₂ <L ₃₇ ).

  In the case of the present embodiment, by configuring in this way, the outer cylindrical surface portion of the outer diameter side before the male screw portion 31 formed near the tip of the intermediate portion of the rod 17 starts to engage with the female screw portion 32. 37 begins to fit into an inner diameter side cylindrical surface portion 36 formed in the middle portion of the circular hole 33. For this reason, even if a metal piece falls off from any of the screw parts based on the screwing of the female screw part 32 and the male screw part 31, the metal piece is placed inside the trunnion 7 and the central part of the rod 17. It does not enter the provided lubricating oil passages 27a and 27b. For this reason, even when the assembly of the toroidal type continuously variable transmission is performed upside down with respect to the state of FIG. 3, the metal piece that has fallen off from any one of the screw parts enters the inner part of the circular hole 33, This metal piece can be prevented from entering the lubricating oil passage 27b formed in the trunnion 7. If the toroidal type continuously variable transmission is assembled with the inner portion of the circular hole 33 facing upward, the above-mentioned consideration is unnecessary (the structure of FIGS. It can sufficiently prevent the metal pieces from being mixed).

  In the case of this embodiment, the tip end portion (lower end portion in FIG. 3) of the pivot 9a provided at one end portion (lower end portion in FIG. 3) of the trunnion 7 and the central portion of the piston 16 constituting the actuator 10 are used. The base end portion (upper end portion in FIG. 3) of the cylindrical portion 42 provided in the base portion 42 is engaged in a state in which relative rotation is prevented. For this reason, in the case of the present embodiment, a cylindrical convex portion 48 is formed in a portion surrounding the opening portion of the circular hole 33 on the distal end surface of the pivot 9 a, and this cylindrical convex portion 48 is formed at the center of the washer 44. The washer 44 is protruded from the side surface with the hole penetrating therethrough. As shown in FIG. 5, outer diameter side flat surfaces 49, 49 are formed at two positions opposite to the diameter direction of the outer peripheral surface of the cylindrical convex portion 48, and the cross-sectional shape of the outer peripheral surface is obscure. It is shaped. On the other hand, as shown in FIG. 5, inner diameter side flat surfaces 50, 50 are formed at two positions opposite to the diameter direction of the inner peripheral surface of the base end portion of the cylindrical portion 42, and a cross section of the inner peripheral surface is formed. The shape is oval. And the outer peripheral surface of the said cylindrical convex part 48 and the proximal end inner peripheral surface of the said cylindrical part 42 are mutually engaged in the state which suppressed the rattling regarding a rotation direction.

In this embodiment, the pivot 9a of the trunnion 7 and the piston 16 are combined concentrically with each other while preventing relative rotation. Then, when the trunnion 7 is pivoted and displaced about the pivot 9a, the piston 16 is smoothly rotated in the cylinder 40 so that the speed change operation of the toroidal continuously variable transmission is stabilized. I have to. If the central axis of the pivot 9a and the central axis of the piston 16 do not coincide with each other, the outer peripheral edge of the piston 16 and the cylinder 40 are displaced when the trunnion 7 swings around the pivot 9a. , And the inner peripheral surface does not slide smoothly, increasing the resistance to the speed change operation. Further, when the pivot 9a and the rod 17 of the trunnion 7 and the piston 16 are relatively rotated, the contact portion between the outer peripheral surface of the rod 17 and the inner peripheral surface of the piston 16 becomes longer with use over a long period of time. There is a possibility of wear. Further, the rod 17 cannot be prevented from coming loose as described below. These inconveniences can be eliminated by matching the two central axes.

  Further, in the case of this embodiment, the cylindrical portion 42 and the rod 17 are engaged in a state in which relative rotation is prevented while the male screw portion 31 and the female screw portion 32 are screwed together and further tightened. It is combined. For this reason, in the case of the present embodiment, after the male screw portion 31 and the female screw portion 32 are screwed together and further tightened, the tip end edge (lower end edge in FIG. 3) of the cylindrical portion 42 is extended over the entire circumference. ) The caulking portion 53 is plastically deformed radially inward, and the caulking portion 53 holds down the flange portion 43 formed at the tip portion of the rod 17. In the case of the present embodiment, by configuring in this way, relative rotation between the trunnion 7 and the rod 17 is prevented via the cylindrical portion 42, and the male screw portion 31 and the female screw portion 32 are screwed together. The part is designed to prevent loosening.

  FIG. 6 shows a third embodiment of the present invention in which some modifications are made to the second embodiment described above. In the case of the present embodiment, male serrations 54 are formed on the outer peripheral surface of the cylindrical convex portion 48a formed on the distal end surface of the pivot 9a, and female serrations 55 are formed on the inner peripheral surface of the proximal end portion of the cylindrical portion 42, respectively. . The male and female serrations 54 and 55 are engaged with each other in a state where rattling in the rotational direction is suppressed. Other configurations and operations are the same as those of the above-described second embodiment, and thus illustrations and explanations regarding equivalent parts are omitted.

  FIG. 7 also shows a fourth embodiment of the present invention in which some changes are made to the second embodiment described above. In the case of the present embodiment, the locking recesses 51, 51 are provided at a plurality of outer peripheral edge portions (four in the illustrated example) of the flange portion 43 formed at the base end portion (lower end portion of FIG. 7) of the rod 17. They are formed at equal intervals in the circumferential direction. On the other hand, locking tongues 52 and 52 are formed at a plurality of positions on the front end edge of the cylindrical portion 42 at the same pitch as the locking recesses 51 and 51. In the case of the present embodiment, after the male screw portion 31 and the female screw portion 32 are screwed together and further tightened (see FIG. 3), the locking tongue pieces 52 and 52 are bent inward in the radial direction of the cylindrical portion 42. The engaging recesses 51, 51 are engaged with each other.

  In the case of this embodiment, the relative rotation prevention between the cylindrical portion 42 and the rod 17 can be achieved more reliably than in the second embodiment described above. However, in order to realize the structure of the present embodiment, the phase of each of the locking recesses 51 and 51 and the locking of each of the locking screw 51 and the female screw 32 are tightened and tightened. It is necessary to match the phases of the tongue pieces 52 and 52. Therefore, it is preferable to implement this embodiment in combination with the third embodiment shown in FIG.

  8 to 9 show Example 5 of the present invention. In the present embodiment, relative rotation between the rod 17 and the cylindrical portion 42 is prevented via the washer 56. For this reason, in the case of the present embodiment, the washer 56 is sandwiched between the flange portion 43 formed at the proximal end portion of the rod 17 and the proximal end surface of the cylindrical portion 42. An inner diameter side locking piece 57 bent in the axial direction is formed on the inner peripheral edge of the washer 56 formed by punching and bending a metal plate, and the inner diameter side locking piece 57 is connected to the cylindrical portion. 42 is engaged with a locking recess 58 formed on the inner peripheral surface of the tip. Therefore, the washer 56 does not rotate with respect to the cylindrical portion 42. A plurality of outer diameter side tongues 59, 59 are formed at equal intervals in the circumferential direction on the outer peripheral edge of the washer 56. Furthermore, a gear-like uneven shape is formed on the outer peripheral surface of the flange 43, for example.

When assembling the structure of the present embodiment, each of the outer diameter side tongue pieces 59, 59, as shown in the chain line of FIG. 8 and FIG. 9, is used when the male screw portion 31 and the female screw portion 32 are screwed together and further tightened. In addition, it is positioned radially outward without being bent. Then, after tightening the male screw portion 31 and the female screw portion 32, the outer diameter side tongue pieces 59, 59 are bent as shown by solid lines in FIG. Engage with. As a result, relative rotation between the rod 17 and the cylindrical portion 42 is prevented.
In this embodiment, there is no structure for preventing relative rotation between the rod 17 and the pivot 9a at the end of the trunnion 7. However, in order to more reliably prevent loosening of the threaded portion between the male screw portion 31 and the female screw portion 32, it is preferable to provide a rotation prevention structure as shown in FIG. 5 or FIG. Other configurations and operations are the same as those of the first and second embodiments described above, and thus redundant description is omitted.

  FIG. 10 shows Embodiment 6 of the present invention. In the case of the present embodiment, the tip of the rod 17 is pushed deeper into the circular hole 33 than in the case of the first embodiment described above. Of the pair of openings existing on the inner peripheral surface of the circular hole 33 of the lubricating oil passage 27b formed in the state where it is inclined in the pivotal wall portion 35 of the trunnion 7 by this tip portion, the lubricating oil The opening on the unnecessary side is blocked for supply. And the plug 47 (refer FIGS. 1-2) required in the case of the said Example 1 is abbreviate | omitted. Other configurations and operations are the same as those in the first embodiment, and thus redundant description is omitted. In addition, it is free to combine the anti-rotation structure as shown in FIGS. 3, 5, 6, 7, and 8 with the structure of the present embodiment.

  FIG. 11 shows Embodiment 7 of the present invention. In the case of the present embodiment, the female screw portion 32 is formed at the back end portion of the circular hole 33 a and the male screw portion 31 is formed at the distal end portion of the rod 17. Correspondingly, a plurality of oil supply grooves 60, 60 that are each long in the axial direction are formed in the axially intermediate portion of the rod 17, and the lubricating oil passage 27b in the trunnion 7 is lubricated from the cylinder body 39 side. Oil can be fed freely. In the case of this example, a part of the oil supply grooves 60, 60 functions as an oil supply passage on the rod 17 side. Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted. In addition, it is also free to combine the anti-rotation structure as shown in FIGS. 3, 5, 6, 7, and 8 with the structure of the present embodiment.

  FIG. 12 shows Embodiment 8 of the present invention corresponding to claims 7-10. In the case of the present embodiment, a male screw portion 61 projects from the center portion of the distal end surface of the pivot 9 a provided at one end portion of the trunnion 7. In addition, a positioning column portion 62 having an outer diameter larger than the outer diameter (thread diameter) of the male screw portion 61 is formed at a portion surrounding the proximal end portion of the male screw portion 61 at the distal end surface of the pivot 9a. Yes. The male screw portion 61 and the positioning column portion 62 are both formed concentrically with the pivot 9a. On the other hand, a screw hole 63 is formed in the center of the tip half (the upper half of FIG. 12) of the rod 17a so as to open to the tip surface of the rod 17a. A positioning cylindrical portion 64 is formed at the tip of the rod 17a. The inner diameter of the positioning cylindrical portion 64 in the free state is the same as or slightly smaller than the outer diameter of the positioning column portion 62.

  The trunnion 7 and the rod 17a as described above are coupled and fixed to each other by screwing the male screw portion 61 into the screw hole 63 and further tightening. In this state, the positioning column 62 is fitted to the positioning cylinder 64 without a gap (with an interference fit), and the pivot 9a and the rod 17a are concentric with each other. Further, between the distal end surface of the pivot 9a and the flange portion 43 formed on the outer peripheral surface of the proximal end portion of the rod 17a, the cylindrical portion 42 provided at the center portion of the piston 16 and the washer 44a are sandwiched.

  Further, in this embodiment, the lubricating oil can be fed into the lubricating oil passage 27b provided in the trunnion 7 by the following structure. For this purpose, a groove 65 is formed in the outer peripheral surface of the tip half of the rod 17a so that one end thereof reaches the tip surface of the rod 17a. An oil passage hole 46 formed in a state where the inner and outer peripheral surfaces of the cylindrical portion 42 communicate with each other in a part of the cylindrical portion 42, and an opening portion of the oil passage hole 46 on the outer peripheral surface of the cylindrical portion 42. A groove 67 formed over the entire circumference at a position aligned with the inner periphery of the cylinder body 39 allows an oil supply port (not shown) provided in the cylinder body 39 to pass through the upstream end of the groove 65. The downstream end of the groove 65 and the lubricating oil passage 27b are formed with a recess 68 formed on a side surface of the washer 44a facing the tip surface of the pivot 9a and a notch 69 formed on the inner periphery. Communicate with each other. For this reason, in the case of the present embodiment, a recess 70 is formed in the upstream end opening of the lubricating oil passage 27b in a circular arc shape that is long in the circumferential direction of the pivot 9a, and the lubricating oil passage 27b and the concave portion are formed. 68 is reliably communicated.

  Also in the case of the present embodiment configured as described above, the metal piece separated from the male screw portion 61 or the screw hole 63 is divided into the concave groove 67, the oil passage hole 46, the concave groove 65, and the cut groove. It will not be mixed into the lubricating oil flowing inside the notch 69, the recess 68, and the lubricating oil passage 27b. For this reason, this metal piece supports the rolling contact portions between the inner surfaces of the input and output disks 2 and 5 and the peripheral surfaces of the power rollers 6 and 6, and the power rollers 6 and 6. The rolling contact portion (see FIGS. 15 to 17) of the rolling bearing can be prevented from being damaged, and the durability of the toroidal continuously variable transmission can be sufficiently secured.

  Also in this embodiment, the central axis of the pivot 9 a provided at the end of the trunnion 7 and the central axis of the rod 17 a based on the fitting of the positioning column part 62 and the positioning cylindrical part 64. Can be matched with high accuracy. Therefore, it is possible to realize a toroidal continuously variable transmission that can perform a shifting operation in a stable state. In this case, it is possible to easily form the outer peripheral surface of the positioning column portion 62 and the inner peripheral surface of the positioning cylindrical portion 64 with high precision by widely used turning, honing, or the like. For this reason, an increase in cost required to stabilize the speed change operation can be suppressed.

  FIG. 13 shows Embodiment 9 of the present invention corresponding to claims 7 to 11. In the case of the present embodiment, the rod 17b is formed in a cylindrical shape, and the screw hole 63a is formed on the inner peripheral surface of the inward flange-shaped flange portion 71 formed near the tip of the inner peripheral surface of the rod 17b. . A lock nut 72 is provided at a portion of the distal end portion of the male thread portion 61 projecting from the central portion of the distal end surface of the pivot shaft 9a provided at one end portion of the trunnion 7 and projecting to the opposite side of the pivot portion 71 from the flange portion 71. And the lock nut 72 is tightened toward one side of the flange 71. The lock nut 72 has a cylindrical shape whose outer peripheral surface can be loosely inserted into the rod 17b, and has a female screw 73 on the inner surface of the front half and a hexagonal hole 74 on the inner surface of the base half. Such a lock nut 72 is inserted into the hexagon hole 74 in the rod 17b in a state where the female screw 73 and the distal end portion of the male screw portion 61 are screwed together by being inserted from the proximal end opening of the rod 17b. Engage the wrench and tighten. According to such a structure of the present embodiment, it is possible to reliably prevent the screw hole 63a and the male screw portion 61 from loosening. Since the configuration and operation of the other parts are the same as those in the above-described eighth embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 14 shows Embodiment 10 of the present invention corresponding to claims 1 to 4. The present embodiment is similar to the second embodiment shown in FIG. 3 described above, but the shape of the lubricating oil passage 27b in the trunnion 7 is different from the second embodiment. Further, in the case of the present embodiment, the fitting portion between the pivot 9a formed at the end portion of the trunnion 7 and the piston 16 of the actuator 10 is not provided with a structure for preventing rotation based on mechanical engagement. That is, the outer peripheral surface of the cylindrical convex portion 48 formed on the distal end surface of the pivot 9a and the inner peripheral surface of the distal end portion of the cylindrical portion 42 attached to the piston 16 are simply cylindrical surfaces. Further, the caulking portion 53 (FIG. 3) as in the second embodiment is not provided at the base end portion of the cylindrical portion. The rotation stopper is based on a frictional force based on screwing / tightening between the male screw portion 31 and the female screw portion 32 as in the first embodiment shown in FIGS. Since other configurations and operations are the same as those in the second embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

Sectional drawing equivalent to the left part of FIG. 17 which shows Example 1 of this invention. The lower enlarged view of FIG. The figure similar to FIG. 2 which shows Example 2 of this invention. The fragmentary sectional view shown in the state which decomposed | disassembled the coupling | bond part of the front-end | tip part of a rod, and a pivot. The disassembled perspective view of the coupling | bond part of a pivot and a cylindrical part. The disassembled perspective view of the coupling | bond part of a pivot and a cylindrical part which shows Example 3 of this invention. The disassembled perspective view of the coupling | bond part of a cylindrical part and a rod base end part which shows the same Example 4. FIG. The figure similar to FIG. 2 which shows the same Example 5. FIG. The top view and sectional drawing of the washer used for Example 5. FIG. The figure similar to FIG. 2 which shows Example 6 of this invention. The figure similar to FIG. 2 which shows the same Example 7. FIG. The figure similar to FIG. 2 which shows the same Example 8. FIG. The figure similar to FIG. 2 which shows the same Example 9. FIG. The figure similar to FIG. 2 which shows the same Example 10. FIG. Sectional drawing which shows an example of the toroidal type continuously variable transmission conventionally known. AA sectional drawing of FIG. BB sectional drawing. FIG. 18 is a cross-sectional view showing a left trunnion of FIG. 17 and parts attached to the trunnion.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Input side disk 3 Ball spline 4 Output gear 5 Output side disk 6 Power roller 7 Trunnion 8 Support shaft 9a, 9b Axis 10 Actuator 11 Support plate 12 Control valve 13 Stepping motor 14 Sleeve 15 Spool 16 Piston 17, 17a, 17b Rod 18 Precess cam 19 Link arm 20 Synchronous cable 21 Drive shaft 22 Press device 23 Support hole 24 Pin 25 Cylindrical part 26 Nut 27a, 27b Lubricating oil passage 28 Cylinder 29 Support hole 30 Radial needle bearing 31 Male thread part 32 Female thread part 33, 33a Circular hole 34 Support plate portion 35 Pivot wall portion 36 Inner diameter side cylindrical surface portion 37 Outer diameter side cylindrical surface portion 38 Housing 39 Cylinder body 40 Cylinder 41a, 41b Hydraulic chamber 42 Cylindrical portion 43 Hook portion 44, 44a Pusher 45 Hexagonal hole 46 Oil passage hole 47 Plug 48, 48a Tubular convex portion 49 Outer diameter side flat surface 50 Inner diameter side flat surface 51 Locking concave portion 52 Locking tongue piece 53 Caulking portion 54 Male serration 55 Female serration 56 Washer 57 Inner diameter Side locking piece 58 Locking recessed part 59 Outer diameter side tongue piece 60 Oil supply groove 61 Male thread part 62 Positioning columnar part 63, 63a Screw hole 64 Positioning cylindrical part 65 Recessed groove 67 Recessed groove 68 Recessed part 69 Notch 70 Recessed part 71 Hook part 72 Lock nut 73 Female thread 74 Hexagonal hole

Claims (11)

  Each of the input side disk and the output side disk supported concentrically so that relative rotation can be freely performed, a plurality of power rollers sandwiched between these two disks, and each of these power rollers supported in a rotatable manner. A plurality of trunnions that are pivotally displaceable around a pivot provided concentrically at both ends, a plurality of actuators for displacing each trunnion in the axial direction of each pivot, and a A plurality of rods for transmitting the movement to each trunnion, and a male thread provided at the tip of each rod is screwed into a female thread provided at the center of the pivot at one end of each trunnion Thus, in the toroidal-type continuously variable transmission in which each trunnion and each rod are coupled, the pivot is formed at one end of each trunnion. Of the central portion, the inner peripheral surface of the circular hole having a bottom which is provided in a state that does not penetrate the end portion in the axial direction, the toroidal type continuously variable transmission, characterized in that the formation of the internal thread portion.   An internal thread portion is formed near the opening of the circular hole, and a part of the circular hole is located on the back side of the internal thread portion with a diameter smaller than the thread diameter of the internal thread portion and on the inner diameter side concentric with the internal thread portion. A cylindrical surface part is formed, and on the part of the rod closer to the tip than the male threaded part, an outer diameter cylindrical surface part that is concentric with the male threaded part and can be fitted internally without rattling is formed. The toroidal continuously variable transmission according to claim 1.   Lubricating oil passages are provided in each trunnion and in each rod to send lubricating oil to the support portion of each power roller. Lubricating oil passages provided in each trunnion and provided in each rod The toroidal continuously variable transmission according to claim 2, wherein the lubricating oil passages communicated with each other.   The toroidal continuously variable transmission according to claim 3, wherein the axial length of the cylindrical surface portion on the outer diameter side is longer than the axial length of the female screw portion.   Each actuator is hydraulic, and a rod is inserted into a cylindrical portion provided at the center of the piston constituting each actuator, and the cylindrical portion is in a state where the male screw portion and the female screw portion are screwed together and further tightened. It is clamped from both sides in the axial direction directly or via a washer between the flange portion of the outward flange provided at the base end of this rod and the end face of the pivot provided at one end of each trunnion. The toroidal continuously variable transmission according to any one of claims 1 to 4, which is engaged with the cylindrical portion in a state in which relative rotation is prevented.   The toroidal continuously variable transmission according to claim 5, wherein the cylindrical portion and the rod are engaged in a state in which relative rotation is prevented while the male screw portion and the female screw portion are screwed and further tightened.   Each of the input side disk and the output side disk supported concentrically so that relative rotation can be freely performed, a plurality of power rollers sandwiched between these two disks, and each of these power rollers supported in a rotatable manner. A plurality of trunnions that are pivotally displaceable around a pivot provided concentrically at both ends, a plurality of actuators for displacing each trunnion in the axial direction of each pivot, and a In a toroidal-type continuously variable transmission comprising a plurality of rods for transmitting movement to each trunnion and connecting each trunnion and each rod, the tip of a pivot provided at one end of each trunnion In the state where the male screw part concentric with the pivot and projecting at the center part of the surface, and the center part of each rod open to the tip face of each rod These rods are connected to the trunnions by screwing the formed screw holes, and the inside of each trunnion is passed through a concave groove formed in the axial direction of each rod on the outer peripheral surface of each rod. A toroidal-type continuously variable transmission characterized in that the lubricating oil can be fed freely into the lubricating oil passage provided in the housing.   Positioning columnar part having an outer diameter larger than the outer diameter of each male threaded portion formed concentrically with this pivotal axis at a portion surrounding the proximal end portion of each male threaded portion at the distal end surface of the pivot shaft provided at one end of each trunnion The center of each rod and the center of the pivot provided at one end of each trunnion are made to coincide with each other by externally fitting a positioning cylindrical portion formed at the tip of each rod. Toroidal continuously variable transmission.   Each actuator is a hydraulic type in which a piston is fitted in a cylinder provided in the actuator body so as to be displaceable in the axial direction of the pivot provided at both ends of each trunnion, and is provided at the center of the piston. A rod is inserted through the cylindrical portion, and a lubricating oil supply path provided in the actuator body and a concave groove formed in the outer peripheral surface of each rod are formed by an oil passage hole that allows the inner and outer peripheral surfaces of the cylindrical portion to communicate with each other. The toroidal continuously variable transmission according to any one of claims 7 to 8, which is in communication.   A washer is sandwiched between the tip end surface of the cylindrical portion provided at the center of the piston and the tip end surface of the pivot provided at one end portion of each trunnion, and the groove formed on the outer peripheral surface of each rod and each trunnion The toroidal continuously variable transmission according to claim 9, wherein a lubricating oil passage provided therein is communicated with a recess formed in a side surface of the washer facing the tip end surface of the pivot. The rod has a cylindrical shape, and the screw hole is formed on the inner peripheral surface of the flange portion of the inward flange formed on the inner peripheral surface end portion of the rod. A lock nut inserted into the rod is screwed into a portion protruding to the opposite side of the pivot, and the lock nut is tightened toward one side surface of the flange portion. The toroidal type continuously variable transmission described in 1.

Images