JP2006307891A - Toroidal type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of improving lubricity of a thrust rolling bearing. <P>SOLUTION: A main body 15 made of synthetic resin of a cage 14 of a thrust ball bearing 8 is composed of a first part 21 and a second part 22 connected mutually and integrally in the direction of thickness. Since a column part 25a of a connection projecting part 25 is extended in the axial direction between mutually facing faces of the first part 21 and the second part 22 connected mutually and integrally in the direction of thickness in the cage 14, a clearance (a lubricating oil passage) 27 having a predetermined interval is provided between the first part 21 and the second part 22. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

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

  In recent years, half-toroidal toroidal continuously variable transmissions have been used as transmission units for automobile transmissions or as transmissions for various industrial machines. FIG. 6 shows a main part of an example of such a toroidal type continuously variable transmission. In the case of the structure shown in the figure, the input side disk 2 and the output side disk 3 are rotatably supported around the input shaft 1 with the inner side surfaces 2a and 3a facing each other. Yes. In addition, a plurality of trunnions 4 are arranged between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3, respectively. It is provided so as to be swingable around a center (not shown). A power roller 6 is rotatably supported by a radial needle bearing 7 and a thrust ball bearing (thrust rolling bearing) 8 around a displacement shaft 5 provided in each trunnion 4.

  The power roller 6 rotates in a state of being sandwiched between the inner side surfaces 2 a and 3 a of the input side disk 2 and the output side disk 3, each of which is a concave surface having an arc cross section, and is output from the input side disk 2. Power is transmitted to the side disk 3. That is, during operation of the toroidal-type continuously variable transmission, the loading cam type pressing device 9 rotates while pressing the input side disk 2 against the output side disk 3 as the rotary shaft 1 rotates. The rotation of the input side disk 2 is transmitted to the output side disk 3 based on the rolling contact between the inner side surfaces 2a and 3a of both the disks 2 and 3 and the peripheral surface 6a of the power roller 6 which is a spherical convex surface. To do. If the trunnion 4 is oscillated and displaced about the pivot axis and the rolling contact position of each surface is changed, the gear ratio between the disks 2 and 3 can be adjusted. That is, as the rolling contact position is set to the inner diameter side of the input side disk 2 and the outer diameter side of the output side disk 3, the speed ratio becomes the deceleration side. On the other hand, as the rolling contact position is set to the outer diameter side of the input side disk 2 and the inner diameter side of the output side disk 3, the speed ratio becomes the speed increasing side.

  When power is transmitted between the input-side disk 2 and the output-side disk 3 as described above, the power roller 6 causes a large radial load and thrust from the inner side surfaces 2a, 3a of both the disks 2, 3. Take the load. In order to support the thrust load among these, a thrust ball bearing 8 is provided between the power roller 6 and the trunnion 4.

  The thrust ball bearing 8 includes an inner ring raceway 10 formed on a large end surface of the power roller 6 (a radially outer surface of the disks 2 and 3 and an upper surface in FIG. 6), and an inner surface of the trunnion 4 (each disk 2 3, the outer ring raceway 12 formed on the inner side surface of the outer ring 11 installed on the lower surface in FIG. 6 on the inner surface in the radial direction, and the inner ring raceway 10 and the outer ring raceway 12 are freely rollable. It comprises a plurality of balls (rolling elements) 13 provided and a cage 14 that holds these balls 13. The retainer 14 includes an annular main body 15 having a uniform wall thickness from the inner peripheral end to the outer peripheral end, and a plurality of pockets 16 provided at equal intervals in the circumferential direction at a radial intermediate portion of the main body 15. The ball 13 is rotatably held in each pocket 16.

During operation of the toroidal type continuously variable transmission, the power roller 6 rotates at a high speed while receiving a strong pressing force from the input side disk 2 and the output side disk 3.
A thrust ball bearing 8 as a power roller bearing of a toroidal-type continuously variable transmission is configured to perform traction contact, and as shown in FIG. 6, there are two locations on the input side disk 2 and the inner side surfaces 2a and 3a of the output side disk 3. A force in the vertical direction (in the direction of arrow A in FIG. 6) is received at the rolling contact portion. The intersecting angle (contact angle) α between the straight lines representing the direction of the force applied at these two positions is smaller than 180 degrees (α <180 degrees). Accordingly, during operation of the toroidal continuously variable transmission, forces in both radial and thrust directions are applied to the power roller 6.

  Of the forces applied to the power roller 6, the power roller 6 is deformed into an elliptical shape as shown exaggeratedly in FIG. 7 based on the force in the radial direction (left-right direction in FIG. 6). Along with such deformation, the inner ring raceway 10 formed on the large end surface of the power roller 6 is similarly deformed. As a result, the contact angle with respect to the ball 13 that is in rolling contact with the inner ring raceway 10 becomes non-uniform in the circumferential direction, and the revolution speed of the ball 13 becomes non-uniform in the circumferential direction. Further, during operation of the toroidal-type continuously variable transmission, the power roller 6 is referred to as so-called 2Ft due to power transmission at the rolling contact portion between the peripheral surface of the power roller 6 and the inner surfaces of the disks 2 and 3. 8A and 8B, a force in the rotational direction of the input side disk 2 as indicated by an arrow B is applied. Then, as shown by an arrow C in FIG. 8B, this force is applied as a moment in a direction in which the rotation center axis of the power roller 6 is tilted together with the displacement shaft 5, and as a result, the rolling surface of the ball 13 and the inner ring raceway 10 and The surface pressure of the rolling contact portion with the outer ring raceway 12 becomes non-uniform. And even by this non-uniform surface pressure, the revolution speed of the balls 13 becomes non-uniform in the circumferential direction.

  As described above, the power roller 6 rotates at a high speed while receiving a complicated and large force. As a result, the revolution speed distribution of the balls 13 constituting the thrust ball bearing 8 is as shown in FIG. In the figure, the magnitude (long and short) of the arrow drawn from the center of the ball 13 represents the magnitude of the revolution speed of the ball 13. As is clear from the figure, the revolution speed of the ball 13 existing on the side on which the force of 2 Ft acts is slower than the revolution speed of the ball 13 existing on the side opposite to the force of 2 Ft acting. The balls 13 are displaced in the circumferential direction of the cage 14 inside the pockets 16 provided in the cage 14 in accordance with such uneven revolution speed.

  In the case of the ball guide system in which the cage 14 is positioned in the axial direction by the ball 13, the difference between the inner diameter of the pocket 16 and the diameter of the ball 13 is very small. In contact with the inner surface. Then, the rolling surface of the ball 13 presses the inner surface of the pocket 16 in the circumferential direction of the cage 14. The magnitude of the pressing force thus generated increases as the difference between the revolution speed of the ball 13 and the rotation speed of the cage 14 increases.

  FIG. 10 shows the distribution in the circumferential direction of the cage 14 of the magnitude of the force (contact load) by which the rolling surface of the balls 13 presses the inner surface of the pocket 16 in this way. In the figure, the magnitude (long and short) of the arrow drawn toward the inner surface of the pocket 16 represents the magnitude of the contact load. As is apparent from the figure, this contact load is large on the side on which the force of 2 Ft acts and on the opposite side, and are opposite to each other with respect to the rotation direction of the cage 14, and the phase is 90 degrees with respect to both sides. It becomes small or zero at the shifted part.

  In this way, in the thrust ball bearing 8 incorporated in the toroidal type continuously variable transmission, the ball 13 causes the column portion 18 existing between the pockets 16 provided in the cage 14 to be on the side where a force of 2 Ft acts. In the opposite direction to the rotation direction of the cage 14, the cage 14 is pushed in the rotation direction of the cage 14 on the side opposite to the side on which the force of 2 Ft acts. Therefore, the column portion is subjected to one cycle of stress load of both swings from compression to tension while the cage 14 makes one rotation. Therefore, unless the strength of the cage 14 is sufficiently secured, the durability of the cage 14 cannot be secured sufficiently, such as a crack in the column portion 18. In view of such circumstances, conventionally, a cage made of metal (mainly made of high-strength brass) having a rigidity at high temperatures and stability against high-temperature traction oil has been used as the cage 14. Yes.

  When the above-described metal machined cage is used as the cage 14 incorporated in the thrust ball bearing 8 in the toroidal-type continuously variable transmission, a sufficient effect can be obtained from the viewpoint of ensuring durability. However, improvement is desired from the viewpoint of weight reduction or cost reduction. That is, when the cage 14 is made of metal, not only the weight of the cage 14 is increased, but also mechanical processing such as cutting and turning, and complicated assembly work such as caulking are required to manufacture the cage 14. I need it. For this reason, in addition to the manufacturing cost of the cage 14 itself, it is inevitable that the assembly cost of the toroidal continuously variable transmission including the cage 14 is increased.

  In consideration of such points, a cage made of synthetic resin and manufactured by injection molding has been developed as a cage that can be manufactured at low cost while improving durability (for example, Patent Document 1 and Patent Document 2). And Patent Document 3).

JP 2003-220711 A Japanese Utility Model Publication No. 6-16753 JP-A-9-42294

  However, in the cages of Patent Documents 1 and 2, since the diameter of the axial intermediate portion of the inner diameter of the pocket is larger than the diameter of the ball, and the diameter of both axial opening portions is larger than the diameter of the ball, the ball 13 Is easily removed from the pocket, and the cage is displaced in the axial direction with respect to the ball 13 and is easily worn by friction with the inner ring raceway 10 and the outer ring raceway 12.

  On the other hand, the cage of Patent Document 3 adopts the above-described ball guiding method, the diameter of the axially intermediate portion of the inner diameter of the pocket is slightly larger than the diameter of the ball, and the opening on the one end side in the axial direction of the pocket is Mulled opening (opening having an opening diameter smaller than that of the ball 13 that allows the ball 13 to be inserted into the pocket while being elastically deformed) and non-muffled opening (it is not possible to insert the ball 13 into the pocket by elastic deformation). Pockets having openings that are significantly smaller than possible balls 13), and the openings at both ends in the axial direction of the cage are made to be openings for opening or not opening for removal. The ball 13 is prevented from falling off.

  However, since the opening of the retainer of Patent Document 3 is elastically deformed, the mold is removed, or the ball 13 is inserted while being elastically deformed, so that the diameter of the opening cannot be made too small. The cage of Patent Document 3 must allow a certain amount of axial displacement. For this reason, when the cage of Patent Document 3 is used for the thrust ball bearing 8 of the power roller 6 in which the inner ring raceway 10 and the outer ring raceway 12 are deformed as described with reference to FIG. 10 and the outer ring raceway 12 are difficult to completely suppress wear due to friction.

Further, during operation of the toroidal type continuously variable transmission, the thrust ball bearing 8 supports a very large thrust load (for example, about 4 tons for an automobile) applied to the power roller 6 and is very high speed (for example, about an automobile). The surface pressure applied to the contact portion between the ball 13 constituting the thrust ball bearing 8 and the inner ring raceway 10 of the power roller 6 and the outer ring raceway 12 of the outer ring 11 is considerably increased. Furthermore, the power roller 6 is elastically deformed as shown in FIG. As a result, the load applied to the thrust ball bearing 8 becomes non-uniform over the circumferential direction. For this reason, since the heat generation at the contact portion described above becomes remarkable, lubricating oil (traction oil) is applied to the thrust ball bearing 8 between the balls 13 and the inner ring raceway 10 of the power roller 6 and the outer ring raceway 12 of the outer ring 11. It is necessary to supply sufficient lubricating oil to the part. In general, the lubricating oil is supplied from the inner diameter side of the thrust ball bearing 8 because the thrust ball bearing 8 rotates at a high speed and the power roller 6 is supported.
However, since the cage of Patent Document 3 is not provided with any oil passage or the like for guiding the lubricating oil supplied to the inner diameter side to the contact portion, there is a risk of poor lubrication of the thrust ball bearing 8.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal continuously variable transmission that can improve the lubricity of a thrust rolling bearing.

  In order to achieve the above object, a toroidal continuously variable transmission according to claim 1 includes an input-side disk and an output-side disk supported concentrically so as to be freely rotatable relative to each other, and sandwiched between these two disks. A power roller, a trunnion that is supported on the inner surface of the power roller so as to be rotatable, and has a trunnion that is swingable about a pivot provided concentrically with each other at both ends. A thrust rolling bearing provided between a side surface and a large end surface of the power roller, and the thrust rolling bearing is disposed on an inner ring raceway formed on the large end surface of the power roller and an inner surface of the trunnion. An outer ring raceway formed on the inner side surface of the outer ring, a plurality of rolling elements provided between the inner ring raceway and the outer ring raceway, and a plurality of rolling elements provided between the inner ring raceway and the outer ring raceway. A retainer made of synthetic resin, and the retainer includes an annular main body, a plurality of pockets that are provided at predetermined intervals in the circumferential direction of the main body and rotatably hold the plurality of rolling elements. The main body of the cage is formed by integrally connecting the annular first part and the second part in the thickness direction by providing a lubricating oil passage therebetween. It is characterized by being.

  In the first aspect of the present invention, since the first part and the second part are integrally joined by providing a lubricating oil passage between them, the inner diameter of the cage is formed. The lubricating oil supplied to the side can be sufficiently supplied to the contact portions of the rolling elements with the inner ring raceway and the outer ring raceway, and the lubricity of the thrust rolling bearing can be improved. Further, since the lubricating oil supplied to the contact portion does not stay in the pocket of the cage and is discharged to the outside through the lubricating oil path, a reduction in friction due to an increase in the agitation resistance of the lubricating oil is prevented. In addition, the cooling performance is improved, and thermal deformation of the resin cage is prevented.

The toroidal type continuously variable transmission according to claim 2 is the invention according to claim 1, wherein the plurality of pockets provided in the first part and the second part face each other part. The pocket opening has an inner diameter slightly larger than the diameter of the rolling element, and the pocket opening on the side away from each part has an inner diameter smaller than the diameter of the rolling element,
The rolling elements are inserted into the plurality of pockets from the side of the pocket opening on the side facing each other part, and the first part and the second part are joined together while sandwiching the plurality of rolling elements. It is characterized by becoming.

  In the invention according to claim 2, since the first and second parts do not have the pocket opening having an inner diameter smaller than the diameter of the rolling element as the opening on the side where the rolling element is inserted, the first and second parts are held against the rolling element. The inner diameter can be made sufficiently small so that the amount of axial displacement of the vessel becomes small. For this reason, the rolling elements are prevented from falling out of the pockets of the first and second parts, and wear of the cage due to friction with the inner ring raceway and the outer ring raceway is prevented.

  In addition, since the rolling elements are inserted into a plurality of pockets from the pocket opening side on the side facing each other part, and the first part and the second part are joined together while sandwiching these rolling elements, It is possible to perform automatic assembly of the cage with high accuracy.

  According to a third aspect of the present invention, the toroidal-type continuously variable transmission according to the first or second aspect of the present invention is configured such that the coupling member that integrally couples the first part and the second part is the first member. It is provided at a position between the plurality of pockets provided in the part and the second part.

  In the invention according to claim 3, the lubricating oil that is about to flow outward from between the adjacent rolling elements is blocked by the coupling member existing in the lubricating oil passage, so that the rolling elements, the inner ring raceway, and the outer ring Since it flows toward the contact portion with the track, a sufficient amount of lubricating oil can be supplied to the contact portion.

  According to a fourth aspect of the present invention, in the invention according to any one of the first to third aspects, the first part and the second part are members having the same shape. It is characterized by.

  In the invention according to the fourth aspect, the cost of parts can be reduced.

  Furthermore, the toroidal continuously variable transmission according to claim 5 is the invention according to any one of claims 1 to 4, wherein the first part and the second part each have a weld portion formed therein. It is characterized by being integrally coupled in the thickness direction so as not to overlap.

  In the invention described in claim 5, the portion where the mechanical properties such as tensile strength are lowered can be dispersed.

  According to the toroidal continuously variable transmission of the present invention, since the lubricating oil passage is provided between the first part and the second part constituting the main body of the cage, the lubricating oil supplied to the inner diameter side of the cage is supplied. In addition, the rolling element can be sufficiently supplied to the contact portion between the inner ring raceway and the outer ring raceway, and the lubricity of the thrust ball bearing can be improved.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The features of the present invention lie in the retainer of the thrust ball bearing, and the other configurations and operations are the same as the conventional configurations and operations described above. Other parts will be described briefly with the same reference numerals as in FIGS.

FIG. 1 is a perspective view showing a cage of a thrust ball bearing (thrust rolling bearing) according to one embodiment of the present invention.
The cage 14 of the present embodiment includes an annular main body 15 and a plurality of pockets that are provided at equal intervals in the circumferential direction at a radial intermediate portion of the main body 15 and each is circular. In each pocket, a ball (rolling element) 13 is rotatably held.

As shown in FIG. 2, the main body 15 includes a first part 21 and a second part 22 that are integrally coupled to each other in the thickness direction.
The first part 21 is a member formed by injection molding of synthetic resin, and a plurality of first part side pockets 23 are formed at equal intervals in the circumferential direction of the intermediate portion in the diameter direction and adjacent to each other. Between the first part side pockets 23, coupling concave portions 24 and coupling convex portions 25 coupled to the second parts 22 are alternately provided at equal intervals.

  The first part-side pocket 23 of the first part 21 has an inner diameter of the inner opening 23a that is open on the side facing the second part 22 and an inner diameter slightly larger than the diameter of the ball 13, and from the second part 22 It is a spherical shape in which the inner diameter of the outer opening 23b opened on the side to be separated is smaller than the diameter of the ball 13. When the first part 21 is injection-molded, a part of the mold in which the first part-side pocket 23 is formed is extracted from the inner opening 23a side, so that the outer opening 23b smaller than the diameter of the ball 13 is removed. Does not elastically deform.

  Further, the coupling recess 24 of the first part 21 is formed in a circular shape with a predetermined depth. Further, as shown in FIG. 3, the coupling part 25 of the first part 21 projects from the column part 25 a that projects toward the second part 22 and from the tip of the column part 25 a, and the coupling recess 24. And a circular protrusion 25b having the same shape as the inner space.

On the other hand, the second part 22 is also a member formed by injection molding of synthetic resin, is a member having the same thickness as the first part 21, and a plurality of parts are equally spaced in the circumferential direction of the intermediate portion in the diameter direction. The second part side pockets 26 are formed, and the coupling recesses 24 and the coupling projections 25 that are coupled to the first parts 21 are alternately provided at equal intervals between the adjacent second part side pockets 26. .
The second part side pocket 26 of the second part 22 has an inner diameter of the inner opening 26 a that is open on the side facing the first part 21, which is slightly larger than the diameter of the ball 13. It is a spherical shape in which the inner diameter of the outer opening 26b opened on the side to be separated is smaller than the diameter of the ball 13. When the second part 22 is injection-molded, a part of the mold in which the second part-side pocket 26 is formed is extracted from the inner opening 26a side, so that the outer opening 26b smaller than the diameter of the ball 13 is removed. Does not elastically deform. Further, the coupling recess 24 and the coupling projection 25 of the second part 22 have the same shape as the coupling recess 24 and the coupling projection 25 formed in the first part 21.
As is apparent from the configuration of the first part 21 and the second part 22 described above, the main body 15 is composed of the first part 21 and the second part 2 having the same shape.

  In order to assemble the cage 14 having the above-described configuration, as shown in FIG. 4, a plurality of balls 13 are inserted into the first part side pocket 23 from the inner opening 23 a side of the first part 21, and the second part 22. The plurality of balls 13 are inserted into the first part-side pocket 26 from the inner opening 26a side of the first part 21, and the circular protrusions 25b of the coupling protrusions 25 of the first part 21 are coupled to the coupling concave parts 24 of the second parts 22. And the circular protrusion 25b of the coupling convex portion 25 of the second part 22 corresponding to the coupling concave portion 24 of the first part 21 is pressed into the first part 21 and the first part 21 while sandwiching the plurality of balls 13 therebetween. Two parts 22 are joined together.

  Here, as shown in FIG. 4, the first part 21 and the second part 22 injected by injecting synthetic resin into the mold are formed with a plurality of welds (joints) w extending in the radial direction. However, the first part 21 and the second part 22 are integrally coupled so that the welds w of the first part 21 and the second part 22 do not overlap (so as not to extend in the same radial direction). ing.

  In the cage 14 assembled as described above, the column part 25a of the coupling convex part 25 extends in the axial direction between the first part 21 and the second part 22 that are integrally coupled in the thickness direction. Therefore, a gap 27 with a predetermined interval is provided between the first part 21 and the second part 22. Since the gap 27 between the first part 21 and the second part 22 is provided so as to communicate from the inner diameter side to the outer diameter side of the main body 15, the lubricating oil supplied to the inner diameter side is used as the rolling surface of the ball 13. The oil roller is an oil passage that leads to a contact portion between the inner ring raceway 10 of the power roller 6 and the outer ring raceway 12 of the outer ring 11 (hereinafter referred to as a lubricating oil passage 27).

  The lubricating oil supplied to the inner diameter side of the cage 14 flows radially outward through the lubricating oil passage 27 provided between the first part 21 and the second part 22 as they rotate. Then, a sufficient amount of lubricating oil is supplied to the contact portion. Here, in the lubricating oil passage 27, the column portion 25 a of the coupling convex portion 25 exists between the adjacent balls 13, and the lubricating oil that tries to flow outward from between the adjacent balls 13 is a column. It is blocked by the portion 25a and flows toward the contact portion. And the lubricating oil supplied to the contact part is discharged | emitted from the outer peripheral side of the lubricating oil path 27 outside, without staying in a contact part.

  Therefore, in the present embodiment, since the lubricating oil passage 27 is provided between the first and second parts 21 and 22, the lubricating oil supplied to the inner diameter side of the retainer 14 is supplied to the balls 13. The rolling contact surface can be reliably supplied to the contact portion between the inner ring raceway 10 of the power roller 6 and the outer ring raceway 12 of the outer ring 11, and the lubricity of the thrust ball bearing 8 can be improved. And, the lubricating oil that is going to flow outward from between the adjacent balls 13 is blocked by the column portion 25a of the coupling convex portion 25 existing in the lubricating oil passage 27 and flows toward the contact portion. A sufficient amount of lubricating oil can be supplied to the contact portion. Further, since the lubricating oil supplied to the contact portion is discharged outside from the outer peripheral side of the lubricating oil passage 27 without staying in the contact portion, it is possible to prevent a reduction in friction due to an increase in stirring resistance, etc. Further, the cooling performance can be improved, and thermal deformation of the resin cage 14 can be prevented.

  Further, by using the main body 15 provided with the lubricating oil passage (gap) 27, the main body 15 can be reduced in weight, and bearing loss due to the collision between the ball 13 and the main body 15 can be reduced.

  Further, the first and second parts 21 and 22 constituting the main body 15 of the cage 14 extract the outer openings 23b and 26b having an inner diameter smaller than the diameter of the ball 13 from the mold during injection molding. Since the opening is not made on the side, and the opening on the side into which the ball 13 is inserted is not made, the inner diameter can be made sufficiently small so that the axial displacement of the cage 14 with respect to the ball 13 becomes small. It becomes. For this reason, it is possible to prevent the balls 13 from falling off from the first part side pocket 23 and the second part side pocket 26 and to prevent wear of the cage 14 due to friction with the inner ring raceway 10 and the outer ring raceway 12. Can do.

  Further, the ball 13 is not deformed by elastically deforming the opening and the ball 13 is forcibly inserted into the first part side pocket 23 and the second part side pocket 26, and the ball 13 from the inner opening 23 a side of the first part 21. Is inserted into the first part side pocket 23, the plurality of balls 13 are inserted into the first part side pocket 26 from the inner opening 26a side of the second part 22, and the first part 21 is sandwiched between the plurality of balls 13. Since the second part 22 and the second part 22 are assembled together, automatic assembly of the cage can be performed with high accuracy.

  Further, the mechanical properties such as the tensile strength of the portion of the first part 21 and the second part 22 where the weld portion w is formed is lower than that of the portion where the weld portion is not formed. This appears remarkably when injection molding is performed with a synthetic resin containing a fibrous filler. Therefore, in the present embodiment, since the first part 21 and the second part 22 are integrally coupled so that the weld parts w do not overlap each other, it is possible to disperse the portion where the mechanical properties deteriorate. Even when injection molding is performed using a normal synthetic resin that does not contain a fibrous filler, since the decrease in tensile elongation is increased in the weld portion, the first part 21 is formed so that the weld portions w do not overlap each other. If the second part 22 is integrally coupled, it is effective for dynamic destruction such as impact and creep.

  Furthermore, since the first part 21 and the second part 22 are composed of members having the same shape, the cost of parts can be reduced.

Next, FIG. 5 is a diagram showing another embodiment of a coupling member that integrally couples the first part 21 and the second part 22.
In the present embodiment, as shown in FIG. 5A, the first part side through hole 30 is formed between the adjacent first part side pockets 23 and the adjacent second part side pockets 26. A second part side through hole 31 having the same inner diameter as that of the first part side through hole 30 is formed therebetween. The coupling member 32 is mounted in the corresponding through holes 30 and 31.

  The coupling member 32 includes a through portion 32a through which the first and second parts side through holes 30, 31 are inserted, and an engaging portion 32b in contact with the outer peripheral edge of the first and second parts side through holes 30, 31. In addition, a plurality of members bent outwardly in a “<” shape are provided at the distal end portion of the penetrating portion 32 a so as to have an outer diameter larger than that of the first and second part side through holes 30, 31. A plurality of members are provided with an expansion / contraction elastic portion 32c that is reduced in diameter while elastically deforming when an external force is applied thereto.

  In order to integrally couple the first part 21 and the second part 22 using the coupling member 32 configured as described above, first, as illustrated in FIG. 5A, the coupling member 32 is inserted into the first part side through hole 30. The through portion 32a is inserted. Next, as shown in FIG. 5B, the expansion / contraction elastic part 32 c of the coupling member 32 is inserted into the second part side through hole 31 of the second part 22 from above. Thereby, the diameter of the expansion / contraction elastic part 32c is reduced while being elastically deformed. And as shown in FIG.5 (c), when the expansion / contraction elastic part 32c which came out from the downward direction of the 2nd part side through-hole 31 expands by elastic return, the 1st part 21 and the 2nd part 22 are predetermined. The gaps (oil passages) 27 are provided while being integrated with each other.

Thus, even if the 1st part 21 and the 2nd part 22 are united together, the same effect as an embodiment shown in Drawing 1-Drawing 4 can be produced.
In addition, as means for integrally connecting the first part 21 and the second part 22, the connection using the connection concave portion 24 and the connection convex portion 25 shown in FIG. 2 or the connection member 32 shown in FIG. 5 was used. Not only the connection but also a connection using bolts, pins, etc., a connection by screwing, a connection by an adhesive, or the like can be appropriately employed.

  The present invention can be applied to various half-toroidal continuously variable transmissions such as a single cavity type and a double cavity type.

It is a perspective view which shows the holder | retainer of the thrust ball bearing which concerns on embodiment of this invention. It is the II-II arrow directional view of FIG. It is a figure which shows the coupling member which couple | bonds the 1st part and 2nd part which concern on embodiment of this invention. It is a perspective view which shows the assembly method of the cage | basket of the thrust ball bearing which concerns on embodiment of this invention. It is a figure which shows the coupling member of the other structure which couple | bonds the 1st part and 2nd part which concern on embodiment of this invention. It is a figure which shows the conventional toroidal type continuously variable transmission, Comprising: It is sectional drawing of the principal part. It is a schematic plan view exaggeratingly showing elastic deformation of a power roller accompanying operation of a toroidal type continuously variable transmission. It is a figure for demonstrating the force added to a power roller with the driving | operation of a toroidal type continuously variable transmission. It is a schematic top view which shows the non-uniform state of the revolution speed of each ball which arises with the driving | operation of a toroidal type continuously variable transmission. It is a schematic plan view which shows the nonuniform state of the force with which a ball presses the pocket inner surface of a holder | retainer.

Explanation of symbols

2 Input disk 3 Output disk 4 Trunnion 6 Power roller (inner ring)
8 Thrust ball bearing (thrust rolling bearing)
10 Inner ring raceway 11 Outer ring 12 Outer ring raceway 13 Ball (rolling element)
14 Cage 15 Main body 21 First part 22 Second part 23 First part side pocket (first part pocket)
23a Inner opening (Pocket opening facing the second part of the first part)
23b Outer opening (pocket opening spaced from second part of first part)
26 2nd part side pocket (2nd part pocket)
26a Inner opening (Pocket opening facing the first part of the second part)
26b Outer opening (pocket opening spaced from first part of second part)
24 coupling recess (coupling member)
25 Joint convex part (joint member)
25a Pillar part 25b Circular protrusion 27 Lubricating oil path 32 Connecting member w Weld part

Claims (5)

An input disk and an output disk that are supported concentrically so that relative rotation can be freely performed, a power roller sandwiched between these two disks, and both ends in a state where the power roller is rotatably supported on the inner surface side. A trunnion that is swingable about a pivot provided concentrically with each other, and a thrust rolling bearing provided between the inner surface of the trunnion and the large end surface of the power roller, The thrust rolling bearing includes an inner ring raceway formed on a large end surface of the power roller, an outer ring raceway formed on an inner side face of an outer ring installed on an inner side surface of the trunnion, and the inner ring raceway and the outer ring raceway. A plurality of rolling elements provided between the rolling elements, and a synthetic resin cage that holds the rolling elements. The cage includes an annular main body, In the toroidal type continuously variable transmission having a plurality of pockets rotatably holding the plurality of rolling elements provided at predetermined intervals in the direction,
The main body of the retainer is formed by providing a lubricating oil passage between the annular first part and the second part and integrally connecting them in the thickness direction. Step transmission. The plurality of pockets provided in the first part and the second part have pocket inner diameters that are slightly larger than the diameter of the rolling elements, and are spaced apart from each other. The pocket opening on the side to be made has an inner diameter smaller than the diameter of the rolling element,
The rolling elements are inserted into the plurality of pockets from the side of the pocket opening on the side facing each other part, and the first part and the second part are joined together while sandwiching the plurality of rolling elements. The toroidal continuously variable transmission according to claim 1, wherein   The coupling member that integrally couples the first part and the second part is provided at a position between the plurality of pockets provided in the first part and the second part. The toroidal continuously variable transmission according to claim 2.   The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein the first part and the second part are members having the same shape.   The said 1st part and the said 2nd part are integrally couple | bonded together in the thickness direction so that the weld part currently formed in each may not overlap. The toroidal type continuously variable transmission described in 1.

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