JP4052103B2 - Toroidal continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a technique for improving durability of a toroidal type continuously variable transmission.
[0002]
[Prior art]
A toroidal-type continuously variable transmission usually includes a pair of input / output disks arranged coaxially and facing each other, and a power roller is interposed between the input / output disks.
The input disk is rotationally engaged on the main shaft by a ball spline or the like so as to be able to stroke, and the output disk is made non-strokeable on the main shaft and is rotatably supported by a bearing such as a needle bearing.
[0003]
For power transmission, the input disk is urged toward the output disk by thrust according to the transmission torque to clamp the power roller between the input and output disks, and the oil film shears between the input and output disks. The power is transferred between the input and output disks.
[0004]
By the way, in order to prevent the above-mentioned bearing that rotatably supports the output disk on the main shaft from coming out of the output disk, conventionally, the above-mentioned bearing is prevented from being detached by a snap ring engaged with the inner periphery of the output disk. It was usual.
[0005]
However, in this case, it is necessary to form a groove for engaging the snap ring on the inner periphery of the output disk, and in combination with the position where the groove is formed near the end of the output disk, There is a possibility that stress concentrates and the durability of the output disk may be lowered, and there is a problem that the size of the output disk must be increased to ensure the durability.
[0006]
Therefore, conventionally, as another configuration for preventing the above-mentioned bearing from coming out of the output disk, for example, the outer periphery of one end of the tubular stopper is fitted to the inner periphery of the input disk facing the output disk, and the other end of the tubular stopper is connected. There has been proposed one that extends to the above-mentioned bearing and prevents the bearing from being removed by the other end of the tubular stopper (see, for example, Patent Document 1).
The above document also describes a configuration in which the ball spline ball is prevented from coming out of the input disk by the one end of the tubular stopper fitted to the inner periphery of the input disk.
[0007]
[Patent Document 1]
Registered Utility Model No. 2595141
[0008]
[Problems to be solved by the invention]
However, in the conventional configuration in which the output disk bearing is prevented from coming off by the other end of the tubular stopper having one end fitted to the inner periphery of the input disk as described above, it has been confirmed that a new problem described below occurs. It was.
[0009]
That is, when the power roller is clamped as described above, the input / output disk tends to be deformed by receiving a bending moment with the distance between the contact point with the power roller and the center of the disk that is the input part of the clamping pressure as the arm length. Due to this deformation, the inner circumference of the input / output disk tends to be deformed into an elliptical shape.
Such deformation causes the tubular stopper to be twisted, and causes the tubular stopper to slide on the output disk and the main shaft and wear quickly, or to drop the tubular stopper from the fitting portion with the input disk. In any case, the durability of the toroidal continuously variable transmission is reduced.
[0010]
In view of the problems caused by the snap ring, the present invention follows the configuration using the tubular stopper as described in the above-mentioned document, but this also slides on or falls off other parts due to the above-described deformation of the input / output disk. An object of the present invention is to propose a toroidal-type continuously variable transmission that has been devised so as to avoid the above-mentioned problems.
[0011]
[Means for Solving the Problems]
  For this purpose, the toroidal continuously variable transmission according to the present invention has the following configuration.
  Of the pair of discs fitted on the main shaft, one of the discs is rotationally engaged on the main shaft so that it can be stroked, and the other disc is disabled on the main shaft to be stroked, and is supported rotatably by a bearing.
  In particular, a tubular stopper to be disposed between the pair of disks is tightly fitted on the main shaft so as to be displaceable in the axial direction.
  In determining the length of the tubular stopper, the tubular stopper has such a length that it can continue to have a bearing stopper function even if it is displaced to the limit position in the direction away from the bearing.And
  At least one of the axial limit positions of the tubular stopper is set by contact between a flange portion provided on the outer periphery of the tubular stopper so as to project between the pair of disks and a corresponding disk end surface.
[0012]
【The invention's effect】
  According to the present invention, the tubular stopper is not fitted to the disk, but is tightly fitted on the main shaft so as to be capable of being stroked to prevent the bearing from coming off. It is possible to avoid the problem that the durability of the toroidal-type continuously variable transmission decreases due to sliding contact with parts or dropping off.Moreover, the adverse effect of the tubular stopper pushing the bearing can be avoided.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
  Less than,Toroidal continuously variable transmissionofOf a reference exampleEmbodiments will be described in detail with reference to the drawings.
  1 to 3 show the present invention.Of a reference exampleFIG. 1 shows a toroidal continuously variable transmission according to an embodiment. As shown in FIG. 1, the toroidal continuously variable transmission has two toroids in a transmission case 1 for doubling the transmission capacity for a vehicle. The transmission unit, that is, the so-called double cavity type toroidal continuously variable transmission in which the front side toroidal transmission unit 2 and the rear side toroidal transmission unit 3 are accommodated in tandem.
[0014]
These toroidal transmission units 2 and 3 include input cone discs (input discs) 4 and 5, output cone discs (output discs) 6 and 7 arranged concentrically facing each other, and power rollers between corresponding input / output cone discs. The same configuration is used with 8 and 9 as main elements.
As clearly shown in FIG. 2, the power rollers 8 and 9 are arranged between the input and output cone disks so as to transmit power by shearing an oil film between the corresponding input and output cone disks as clearly shown in FIG. 2 for the power roller 8 of the front side toroidal transmission unit 2. The rotation axis O of the input / output cone disk is interposed.₃Oppositely arranged on both sides of the.
[0015]
As shown in FIG. 1, the front side toroidal transmission unit 2 and the rear side toroidal transmission unit 3 are arranged coaxially so that the output cone disks 6 and 7 are back to back, and in this arrangement, the main shaft 10 is placed in the transmission case 1. And the input / output cone disks 4 to 7 of the toroidal transmission units 2 and 3 are supported on the main shaft 10.
Each of the front side input cone disk 4 and the rear side input cone disk 5 is rotationally engaged with the main shaft 10 by the ball spline 11 but is slidable in the axial direction, and the rear side input cone disc 5 is screwed to the main shaft 10. The nut 12 prevents it from coming off.
[0016]
Further, the output cone disks 6 and 7 are integrally coupled to each other via the hollow output shaft 13, and the hollow output shaft 13 and the needle bearing are allowed to be supported by rotatably supporting the hollow output shaft 13 on the main shaft 10. The output cone discs 6 and 7 are supported on the main shaft 10 so as not to be displaceable in the axial direction by the bearings 51 that rotate.
[0017]
The power rollers 8 and 9 are arranged to transfer power by shearing the oil film between the corresponding input / output cone disks 4 and 6 and 5 and 7 as described above. It is rotatably supported on each trunnion 14,15.
Although the detailed shape of the trunnion 14 that rotatably supports the power roller 8 of the front side toroidal transmission unit 2 is shown in FIG. 2, a trunnion 15 that rotatably supports the power roller 9 of the rear side toroidal transmission unit 3 is shown. The same applies to the shape.
[0018]
Both the trunnions 14 of the front-side toroidal transmission unit 2 and both the trunnions 15 of the rear-side toroidal transmission unit 3 share the same upper end adjacent to each other on the same side (the upper side close to the top wall of the transmission case 1). The plate-like upper link 16 is articulated at the four corners.
For this reason, the plate-like upper link 16 has a planar shape, and openings 16a (see FIG. 2) through which the upper ends of the trunnions 14 and 15 enter are formed at the four corners.
The two trunnions 14 of the front side toroidal transmission unit 2 and the trunnions 15 of the rear side toroidal transmission unit 3 are further provided at the four corners of the plate-like lower link 17 that is common to all the lower ends adjacent to each other on the opposite lower side. As shown in FIG. 2, the plate-like lower link 17 has a planar shape similar to that of the plate-like upper link 16, and openings 17a into which the lower ends of the trunnions 14 and 15 enter at the four corners. Drill.
[0019]
When the upper and lower ends of the trunnions 14 and 15 are connected to the openings 16a and 17a of the plate links 16 and 17, the outer spherical surface of the spherical joint 18 is fitted into the openings 16a and 17a as shown in FIG. A rotary bearing 19 is interposed between the spherical joint 18 and the upper and lower ends of each trunnion 14, 15, and the upper and lower ends of each trunnion 14, 15 are connected to the plate-like links 16, 17 by a composite joint constituted by them. On the other hand, it is articulated so that it can rotate and change its angle of intersection.
The plate-like links 16 and 17 are driven out from the corresponding input / output cone disks by the clamping force between the input / output cone disks 4 and 6 to which the power rollers 8 and 9 correspond. It works to be safe.
[0020]
As shown in FIGS. 1 and 2, link supports 20 and 21 are attached to the transmission case 1 with bolts 22 and 23 between the upper ends of the paired trunnions 14 and between the upper ends of the paired trunnions 15. The link supports 24 and 25 are attached to the transmission case 1 by bolts 26 between the lower ends of the trunnions 15 and between the lower ends of the trunnions 15.
As shown in FIGS. 1 and 2, the plate-like link 16 is formed with openings 16b through which the link supports 20 and 21 penetrate, and the plate-like link 17 also has link supports 24 and 25 as shown in FIGS. A similar opening 17b is formed.
[0021]
Pins 27 projecting in the axial direction of the main shaft 10 from the respective outer surfaces are planted on the link supports 20 and 21, and pins 28 are also fitted to the link supports 24 and 25. 16 and 17 are supported with respect to the transmission case 1, but the holes 16c and 17c provided in the plate-like links 16 and 17 so that the pins 27 and 28 penetrate therethrough are oblong and long in the longitudinal direction of the trunnions 14 and 15. The links 16 and 17 are supported so as to be displaceable in the same direction.
[0022]
According to such a support structure, since the plate-like links 16 and 17 can be displaced in the longitudinal direction of the trunnions 14 and 15, there is a possibility that the movement is hindered by interference with parts other than the trunnions 14 and 15.
In order to eliminate this concern, the trunnions 14 and 15 restrict the displacement of the plate links 16 and 17 in the same direction. That is, as shown in FIG. 2, a stepped portion (only the stepped portion 14a of the trunnion 14 is visible in FIG. 2) provided to receive the spherical joint 18 and the rotary bearing 19 at the upper ends of the trunnions 14 and 15, and a plate-like upper link The plate-like upper link 16 is sandwiched between the upper ends of the trunnions 14 and 15 projecting from the opening 16a of the 16 and the stopper plate 30 attached by the bolts 29, so that the plate-like upper link 16 is displaced in the trunnion longitudinal direction. To regulate.
[0023]
As for the regulation of the plate-like lower link 17, as shown in FIG. 2, a step portion provided to receive the spherical joint 18 and the rotary bearing 19 at the lower ends of the trunnions 14, 15 (only the step portion 14b of the trunnion 14 in FIG. 2). And the plate-like lower link 17 between the front and rear unit shift synchronization (tilt synchronization) wire pulley 31 fixed to the lower ends of the trunnions 14 and 15 protruding from the opening 17a of the plate-like lower link 17. These restrict the displacement of the plate-like lower link 17 in the trunnion longitudinal direction.
[0024]
As shown in FIG. 1, an output gear housing 32 as an intermediate wall is arranged between the output cone disks 6 and 7 arranged back to back with each other, and this is attached to the transmission case 1 with bolts 33. An output gear 34 that is integrally formed on the outer periphery of the hollow output shaft 13 is accommodated in 32. At the same time, the gear housing 32 rotatably supports the central portion of the main shaft 10 with respect to the transmission case 1 via the hollow output shaft 13 by the ball bearing 35.
A counter gear 36 is engaged with the output gear 34, and this gear is coupled to the counter shaft 37, so that the transmission power from the toroidal type continuously variable transmission is taken out from the counter shaft 37.
[0025]
The transmission input rotation transmitted from the left side in FIG. 1 is input to the input cone disks 4 and 5 of both toroidal transmission units 2 and 3 via the loading cam 38.
The loading cam 38 is provided with a cam flange 39, which is coaxially provided on the rear surface of the front side input cone disk 4, and is rotatably supported on the main shaft 10 by a radial and thrust bearing 40. It is assumed that a cam roller 41 is interposed between the flanges 39.
The loading cam 38 transmits the input rotation to the front-side input cone disk 4 and to the rear-side input cone disk 5 via the main shaft 10, and by relative rotation of the cam flange 39 and the cone disk 4 according to the transmission torque. Thrust in the direction toward the output cone disc 6 is given to the input cone disc 4,
The thrust reaction force at this time reaches the rear input cone disc 5 from the cam flange 39 through the radial / thrust bearing 40, the main shaft 10 and the nut 12 which rotatably support the main shaft 10 to the rear input cone disc 5 in this order. The input cone disk 5 is biased toward the output cone disk 7.
Therefore, the power rollers 8 and 9 are clamped between the corresponding input / output cone discs with a force corresponding to the transmission torque, thereby enabling the power transmission between the corresponding input / output cone discs.
[0026]
As shown in FIG. 2 showing the front-side toroidal transmission unit 2, a servo piston 42 is further coaxially coupled to the lower ends of the trunnions 14 and 15, and these servo pistons 42 are in phase (same shift direction) by the control valve 43. It is assumed that well-known shift control is performed by making the strokes synchronously.
In the following, the speed change operation will be described in brief. The input rotation is transmitted to the front side input cone disk 4 via the loading cam 38, and the rotation to the input cone disk 4 is simultaneously performed on the rear side via the ball spline 11 and the main shaft 10. The same is transmitted to the input cone disk 5 as well.
The rotation of the input cone disks 4 and 5 is transmitted to the power rollers 8 and 9 engaged therewith through the shearing of the oil film.₁The power rollers 8 and 9 transmit the rotation to the output cone disks 6 and 7 engaged therewith through the oil film shear, and this rotation is transmitted from the common output gear 34 to the counter gear 36. The counter shaft 37 is reached, and power can be taken out from the counter shaft.
[0027]
Here, the power rollers 8 and 9 are synchronized by the servo piston 42 via the trunnions 14 and 15, and the power roller rotation axis O₁Swing axis O₂In the same phase in the direction of, the stroke from the non-shifting position shown in FIG. 1 and FIG.₁Cone disc rotation axis O₃When offset from, the power rollers 8, 9₂Are tilted in the same phase in synchronization with each other.
As a result, the contact locus circular radius of the power rollers 8 and 9 with respect to the input / output cone disk continuously changes, and the transmission ratio between the input / output cone disks 4 and 6 and the transmission ratio between the input / output cone disks 5 and 7 are changed. You can keep it the same and change it steplessly.
When the transmission ratio reaches a predetermined transmission ratio, the transmission ratio can be maintained by returning the power rollers 8 and 9 to the initial stroke position at offset 0.
[0028]
In the present embodiment, as shown also in FIG. 1, as clearly shown in FIG. 3, the rear side toroidal transmission unit 3 includes bearings 51 related to the output cone disks 6 and 7 of both toroidal transmission units 2 and 3, and the input. A configuration for preventing the balls (rotating engagement elements) 11a of the ball splines 11 related to the cone disks 4 and 5 from coming out of the corresponding cone disks is particularly as follows.
[0029]
That is, a tubular stopper 52 is fitted on the main shaft 10 between the paired input / output cone discs, and the tubular stopper 52 responds to the displacement of the input cone discs 4 and 5 in the axial direction. 10 is tightly fitted in a clearance fit type.
[0030]
Then, the length of the tubular stopper 52 indicated by L in FIG. 3 is determined as follows. That is, when the tubular stopper 52 is displaced in the direction away from the bearing 51 to the limit position (in the illustrated case, the position where the tubular stopper 52 is in contact with the ball spline 11), the bearing 51 is also moved from the inner periphery of the output cone disks 6 and 7. The length L of the tubular stopper 52 is determined so that it can continue to have a bearing stopper function to prevent it from coming out,
Further, even when the tubular stopper 52 is displaced to the other axial limit position in contact with the bearing 51, the ball (rotating engagement element) 11a of the ball spline 11 is prevented from coming out from the inner periphery of the input cone disks 4 and 5. The length L of the tubular stopper 52 is determined so that the rotation engagement element stopper function can be continued.
[0031]
Moreover, between the outer peripheral surface in the edge part of the tubular stopper 52 which will enter in the center hole of the cone discs 4-7 by the length L determined as mentioned above, and the inner peripheral surface of a corresponding cone disc As shown in FIG. 3, set the gaps α and β,
These gaps α and β are necessary to prevent the inner peripheral surface of the cone disk from interfering with the outer peripheral surface of the end of the tubular stopper 52 even when the cone disk is deformed by the power roller clamping pressure. Use a minimum gap.
[0032]
  Such a bookReference exampleAccording to the embodiment, the tubular stopper 52 for preventing the bearing 51 from coming out of the output cone disks 6 and 7 is not fitted on the inner periphery of the cone disk as described in the above document, but on the main shaft 10. Due to the tight fit so that the stroke can be achieved, the tubular stopper 52 will not be distorted by the deformation of the cone disk caused by the clamping pressure of the power roller. As a result, the tubular stopper 52 slidably contacts or falls off to other parts. The problem of reducing the durability of the continuously variable transmission can be avoided.
[0033]
In addition, according to the present embodiment, the tubular stopper 52 is not fitted to the inner periphery of the cone disk as described in the above-mentioned document, and the tubular stopper 52 is closely fitted on the main shaft 10 for the same structural reason. The diameter can be reduced, contributing to the reduction in size and weight of the toroidal-type continuously variable transmission.
[0034]
Furthermore, according to the present embodiment, the tubular stopper 52 also functions as a rotation engagement element stopper that prevents the ball (rotation engagement element) 11a of the ball spline 11 from slipping out from the inner periphery of the input cone disks 4 and 5. Therefore, the rotational engagement element stopper which has been conventionally required can be omitted, which is advantageous in terms of cost.
[0035]
In addition, according to the present embodiment, since the gaps α and β are set between the outer peripheral surface of the end of the tubular stopper 52 and the corresponding inner peripheral surface of the cone disk, the cone disk accompanying the power roller clamping pressure is set. The disc inner peripheral surface does not interfere with the end outer peripheral surface of the tubular stopper 52 even by the deformation of 4 to 7, and the tubular stopper 52 slides on the cone discs 4 to 7 to improve the durability of the toroidal continuously variable transmission. The problem of lowering can be avoided.
[0036]
  FIG. 4 (a) and FIG.1In the present embodiment, the embodiment is shown.In addition to the configuration of the previous reference example,A flange portion 52 a is provided on the outer periphery of the tubular stopper 52 so as to project between the paired input / output cone disks 4, 6 and 5, 7.
  As shown in FIG. 4A, the flange portion 52a is used to define the axial limit position of the tubular stopper 52 in the direction away from the bearing 51 by abutting against the end face of the corresponding input disk 5 (4). ,
  Also, as shown in FIG. 4B, the other axial direction limit position of the tubular stopper 52 in the direction approaching the bearing 51 is defined by abutting against the end face of the corresponding output disk 7 (6).
[0037]
Here, the width W and the position of the flange portion 52a are determined so that the flange 52a can continue to have a function of preventing the bearing 51 from coming off even at the axial limit position of the tubular stopper 52 shown in FIG. 4B, it is determined that the tubular stopper 52 can continue to have a function of preventing the ball 11a from coming off even at the limit position in the axial direction of the tubular stopper 52 shown in FIG.
[0038]
  Book number1According to the embodiment, the axial limit position of the tubular stopper 52 is defined by the contact between the outer peripheral flange portion 52a of the tubular stopper 52 and the corresponding end face of the cone disk, so that the tubular stopper 52 pushes the bearing 51. The adverse effect of moving or limiting the movement range of the ball 11a can be avoided.
[0039]
  5 (a), 5 (b) and FIG.2In the present embodiment, unlike the case of the above embodiment, the tubular stopper 52 is shortened to only prevent the bearing 51 from being removed, and the ball 11a has no retaining function.
  Therefore, a dedicated ball retaining ring 53 for retaining the ball 11a is provided on the main shaft 10 in the same manner as in the prior art.
[0040]
Also in the present embodiment, the same flange portion 52a as described above is provided on the outer periphery of the tubular stopper 52 to define the axial limit position of the tubular stopper 52. However, the axial direction of the tubular stopper 52 shown in FIG. A radial oil groove 52b is formed on one side surface of the flange portion 52a that comes into contact with the end surface of the input disk 5 (4) at the limit position, as shown in FIGS.
Further, as shown in FIG. 5B, a radial oil groove 52c is formed on the other side of the flange portion 52a that abuts against the end face of the output disk 7 (6) at the axial limit position of the tubular stopper 52 shown in FIG. 5B. To do.
[0041]
  The first formed with such radial oil grooves 52b and 52c.2According to the embodiment, even when the tubular stopper 52 is in any axial limit position, the oil flow is generated radially outward from the ball spline 11 and the bearing 51 as indicated by arrows γ and δ. In addition, the presence of the flange 52a does not cause poor lubrication or cooling of the bearing 51 or the ball spline 11.
[0042]
Incidentally, as described above, the deformation of the cone disk caused by the clamping force of the power roller also causes the interference between the inner peripheral surface of the cone disk and the outer peripheral surface of the end of the tubular stopper 52, and the sliding between the tubular stopper 52 and other parts. In order to avoid contact more reliably, it is desirable to set a sufficiently large gap in the radial direction and the axial direction of the tubular stopper 52 that is larger than the gaps α and β in the previous embodiment.
However, when such a large gap is set, it is conceivable that the tubular stopper 52 is not stabilized during rotation and suddenly contacts the main shaft 10 and the input / output cone disks 4 to 7 to generate sound and vibration.
In particular, when the gap between the tubular stopper 52 and the bearing 51 is increased, the bearing 51 is greatly tilted and the skew is rapidly increased, which may increase friction and decrease the life of the bearing.
Therefore, even when a sufficiently large gap is set in the radial direction and the axial direction of the tubular stopper 52, in the following embodiment, in order to stabilize the tubular stopper 52 at the time of rotation, a configuration using an elastic body is used. To do.
[0043]
  7 and 8 show the first aspect of the present invention.3In the present embodiment, as shown in FIG. 7, the main shaft 10 is disposed between the input / output cone disks 4, 6 and 5, 7 which are paired as in the previous embodiment. Tubular stoppers 52 are fitted on top, and these tubular stoppers 52 are tightly fitted on the main shaft 10 in a clearance fit type in response to the axial displacement of the input cone disks 4 and 5. Further, in the present embodiment, the rear side toroidal transmission unit 3 shown in FIG. 7 is interposed between the inner peripheral surfaces of the paired input / output cone disks 4, 6 and 5, 7 and the outer peripheral surface of the tubular stopper 52. As clearly shown in FIG. 8, a gap ε described later is set. Although not shown, the front side toroidal transmission unit 2 has the same configuration as that of the rear side toroidal transmission unit 3.
[0044]
Furthermore, in the present embodiment, a sufficient gap is provided between the bearing 51 and the tubular stopper 52 in consideration of the axial movement of the input disk 5 (4), and a plurality of compression springs as elastic bodies are provided in this gap. And a ball bearing 55 as a bearing for supporting a thrust force is interposed between the coil spring 54 and the tubular stopper 52. Although not shown, six coil springs 54 are arranged on the outer periphery of the main shaft 10 at equal intervals here. Thereby, a uniform elastic force by the coil spring 54 can be applied to the bearing 51 and the tubular stopper 52.
[0045]
  Note that the gap ε can reliably prevent the inner peripheral surface of the cone disk from interfering with the outer peripheral surface of the end of the tubular stopper 52 even when the cone disk is deformed due to the clamping force of the power roller as described above. ,PreviousReference exampleThe gaps α and β (see FIG. 3) in the embodiment are set sufficiently larger.
[0046]
  In addition, the tubular stopper 52 has the first2In the embodiment, like the one shown in FIG. 5, a flange portion 52 a that defines the axial limit position of the stopper is provided. The flange portion 52a is urged by the elastic force of the coil spring 54 so as to come into contact with the end surface of the input cone disk 5 (4). Thereby, the tubular stopper 52 prevents the ball 11a of the ball spline 11 from coming off and prevents the bearing 51 from coming out of the output cone disk 7 (6). The length L of the tubular stopper 52 and the width W of the flange portion 52a are set in consideration of the amount of axial movement of the input cone disk 5 (4) and the corresponding elastic force of the coil spring 54.
[0047]
  Therefore, this book3According to the toroidal continuously variable transmission of the embodiment, as described above, the coil spring 54 is provided between the bearing 51 and the tubular stopper 52 that rotatably support the output cone disk 7 (6) on the main shaft 10. A uniform elastic force by the coil spring 54 is applied to the bearing 51 and the tubular stopper 52.
[0048]
  Therefore, the tubular stopper 52 interferes with the members disposed in the vicinity thereof in consideration of the deformation of the disk by clamping the power rollers 8 and 9 between the paired input / output cone disks 4 and 6 and 5 and 7. Even when the radial and axial gaps of the tubular stopper 52 are sufficiently large so that the stopper 52 itself is not rotated, the stability of the stopper 52 itself during rotation can be improved. Abrupt contact with disk 5 (4), 7 (6)ShiIt is possible to suppress generation of noise and vibration, and to suppress wear of members. Further, since the bearing 51 can be prevented from being tilted by increasing the gap between the tubular stoppers 52, the skew of the bearing 51 can be reduced, the life of the bearing 51 can be improved, and the friction can be reduced. it can.
[0049]
In addition, in the toroidal type continuously variable transmission according to the present embodiment, a ball bearing 55 as a bearing is provided between one end of the coil spring 54 and the tubular stopper 52. Thereby, even if the members rotating relatively are in contact with each other, friction can be suppressed and wear of the members can be prevented. In the present embodiment, the ball bearing 55 is interposed between the coil spring 54 and the tubular stopper 52. However, instead of this configuration, the end of the coil spring 54 on the output cone disk 7 (6) side is provided. Even if the coil spring 54 is interposed between the bearing 51 and the bearing 51, the same operation and effect as in the present embodiment can be obtained.
[0050]
  Figure 9 shows this3The principal part of the modification of the toroidal-type continuously variable transmission in embodiment is shown. In this modification, a lubricity improving member 56 such as an oil-impregnated alloy, which is a plain bearing, is interposed between the coil spring 54 and the tubular stopper 52 instead of the ball bearing 55 in the above embodiment. According to the toroidal type continuously variable transmission having such a configuration,3In addition to being able to obtain the same effects as those of the embodiment, the lubricity improving member 56 can have a simple shape and can be manufactured at low cost.
[0051]
  FIG. 10 shows the first aspect of the present invention.4It is principal part sectional drawing of the toroidal type continuously variable transmission which becomes embodiment. First3In the present embodiment, the coil spring 54 is interposed between the bearing 51 and the tubular stopper 52. However, in this embodiment, a plurality of coil springs 54 are replaced with the ball bearing 55 and the ball spline 11 in this embodiment. Between the two. The previousEmbodiment of reference example and first to thirdComponents having the same configuration as the embodiment are given the same reference numerals.
[0052]
  Since the plurality of coil springs 54 are interposed between the balls 11 a of the ball spline 11 and the tubular stopper 52, the same number of coil springs as the number of strips of the ball spline 11 are used. In the present embodiment as well,3Similar to the embodiment, six coil springs 54 are arranged at equal intervals on the outer periphery of the main shaft 10.
[0053]
  Book of the above configuration4According to the toroidal type continuously variable transmission of the embodiment, the ball 11a of the ball spline 11 comes out of the input cone disk 5 (4) by the elastic force of the coil spring 54 interposed between the ball bearing 55 and the ball spline 11. The flange 52a of the tubular stopper 52 is urged through the ball bearing 55 so as to abut against the tip of the output cone disk 7 (6). Therefore, the ball 11a of the ball spline 11 can be prevented from coming out of the input cone disk 5 (4), and the bearing 51 can be prevented from coming out from the output cone disk 7 (6).
[0054]
  FIG. 11 shows the present4The principal part of the modification of the toroidal-type continuously variable transmission of embodiment is shown. In this modification, the coil spring 54 is interposed between the tip of the input cone disc 5 (4) and the ball bearing 55, that is, the tip of the input cone disc 5 (4) is interposed via the ball bearing 55. The coil spring 54 is interposed between the portion and the tubular stopper 52. The balls 11 a of the ball spline 11 are prevented from coming off by a ball retaining ring 53 fitted in a circumferential groove provided on the main shaft 10.
[0055]
According to the configuration of this modification, in addition to obtaining the same operation and effect as the present embodiment, the area that can support the end of the coil spring 54 of the tubular stopper 52 and the input cone disk 5 (4). Can be made larger. That is, since the input cone disc 5 (4) is supported by the main shaft 10 by the ball spline 11, the tip portion of the input cone disc 5 (4) is larger than the output cone disc 7 (6) supported by the main shaft 10 via the bearing 51. Wide area. Therefore, since the area that can be supported by the coil spring 54 can be increased, the layout of the coil spring 54 as an elastic body can be improved in the radial direction of the shaft.
[0056]
Accordingly, the diameter of each of the plurality of coil springs 54 can be increased, which is advantageous when it is desired to further reduce the spring coefficient of the elastic body. Further, the present invention is not limited to the case where a coil spring is used as the elastic body, but is advantageous in a configuration using a specially shaped spring as described later.
[0057]
  FIG. 12 shows a toroidal-type continuously variable transmission according to the present invention.5The principal part of embodiment is shown. First3Embodiment and first4In the embodiment, the configuration is such that a plurality of coil springs 54 are used as the elastic body. However, in the present embodiment, the elastic body has a drum shape that gradually decreases in diameter toward the center. Therefore, a plate spring 57 having a special shape in which an end portion on the output cone disk 7 (6) side is folded outward is used. Although not shown, the leaf spring 57 is provided with a plurality of slits extending in the axial direction in the circumferential direction, so that the diameter of the spring can be increased or decreased as a whole. Further, the balls 11 a of the ball spline 11 are prevented from coming off by a ball retaining ring 53 fitted in a circumferential groove provided on the main shaft 10.
[0058]
Here, the leaf spring 57 is disposed in contact with the main shaft 10 and the inner peripheral surface of the tubular stopper 52. Thereby, the tubular stopper 52 is supported from the radial direction and the axial direction by the reaction force from the leaf spring 57. In addition, the same code | symbol is attached | subjected to what has the same structure as previous embodiment.
[0059]
  Therefore, this book5According to the toroidal-type continuously variable transmission of the embodiment, since the plate spring 57 having a special shape is interposed between the main shaft 10 and the tubular stopper 52, the tubular stopper 52 is axially moved by the elastic force of the plate spring 57. It can be supported from the direction and the radial direction. Thereby, the tubular stopper 52 can be more stably supported with respect to the main shaft 10 especially in the radial direction. Therefore, sound and vibration due to the collision between the tubular stopper 52 and the main shaft 10 can be more effectively suppressed.
[0060]
  Further, FIG. 13 shows the first of the toroidal type continuously variable transmission of the present invention.6The principal part of embodiment is shown. In the present embodiment, the previous first shown in FIG.5In the configuration of the embodiment, instead of the leaf spring 57, a leaf spring 58 having a special shape in the shape of a crown whose intermediate portion is enlarged in the axial direction is used as an elastic body. Here, the main shaft 10 is assembled after the leaf spring 58 is interposed between the outer peripheral portion of the shaft portion 52d of the tubular stopper 52 and the inner peripheral portion of the output cone disk 7 (6). The above5Similar to the embodiment, the leaf spring 58 is provided with a plurality of slits (not shown) extending in the axial direction in the circumferential direction so that the entire spring can be expanded and contracted.
[0061]
  Therefore, this book6According to the toroidal type continuously variable transmission of the embodiment, the tubular stopper 52 is stable in the axial direction and the radial direction by the elastic force of the leaf spring 58 interposed between the output cone disk 7 (6) and the tubular stopper 52. To be supported. Moreover, the main shaft 10 is assembled after the tubular stopper 52 is provided on the inner periphery of the output cone disk 7 (6). As a result, in the assembly process, it is required that the inner diameter of the output cone disk 7 (6) and the inner diameter of the tubular stopper 52 be arranged concentrically. However, according to the toroidal-type continuously variable transmission of the present embodiment. For example, a uniform reaction force can be applied to the tubular stopper 52 from the circumferentially provided leaf spring 58. Thereby, since the tubular stopper 52 can be stably supported on the main shaft 10, the tubular stopper 52 can be prevented from being twisted.
[0062]
  In addition, FIG.6The principal part of the modification of the toroidal-type continuously variable transmission of embodiment is shown. This modification is the same as that shown in FIG.6In the configuration of the embodiment, the inner diameter portion of the output cone disk 7 (6) on which the tubular stopper 52 is mounted is configured as a stepped shape including a latching portion 7a (6a) projecting radially inward. is there. Note that those not described here are those shown in FIG.6The configuration is the same as in the embodiment.
[0063]
Therefore, according to the toroidal type continuously variable transmission of this modification, the inner diameter portion of the output cone disk 7 (6) to which the tubular stopper 52 is attached is provided with the latching portion 7a (6a) projecting radially inward. Since the stepped shape is adopted, the leaf spring 58 can be pushed and supported radially inward of the tubular stopper 52 by the latching portion 7a (6a). Thereby, especially at the time of an assembly | attachment, it can prevent reliably that the leaf | plate spring 58 falls from the tubular stopper 52, and can improve an assembly | attachment property.
[0064]
  In addition, FIG.6The principal part of the further modification of the toroidal-type continuously variable transmission in embodiment is shown. In this modification, the tubular stopper 52 used in the previous embodiment is formed of an elastic body. That is, the tubular stopper 59 here is constituted by a leaf spring having a stopper portion 59a having an L-shaped cross section and a folded portion 59b fitted to the inner peripheral portion of the output cone disk 7 (6). The tubular stopper 59 has a stopper function for preventing the bearing 51 from coming out of the output cone disk 7 (6), and is shown in FIG.6Similar to the leaf spring 58 of the embodiment, it has a function of an elastic body having a shape in which an end portion arranged on the output cone disk 7 (6) side is bent radially outward. The tubular stopper 59 is fitted to the inner peripheral portion of the output cone disk 7 (6) and disposed between the paired input / output cone disks 4, 6 and 5, 7.
[0065]
Therefore, according to the toroidal type continuously variable transmission of this modification, the tubular stopper 59 is formed by integrally forming the tubular stopper and the elastic body, so that the number of parts can be reduced and the cost can be reduced. It can be set as a simple structure.
[0066]
  Although described above based on the illustrated examples, the present invention is not limited to the above embodiment.EtIs not something For example, in each of the above embodiments, the case where the toroidal continuously variable transmission is configured as a double cavity type toroidal continuously variable transmission has been described. However, the single cavity type toroidal type having only one toroidal transmission unit is described. The above idea of the present invention can be similarly applied to the case of a continuously variable transmission.
[0067]
In the above embodiment, the input cone discs 4 and 5 are rotatably engaged with the main shaft 10 by the ball spline 11 and the output cone discs 6 and 7 are rotatable on the main shaft 10 by the bearing 51 in a stroke impossible state. The idea of the present invention was applied to a toroidal type continuously variable transmission of the type supported by the above. However, on the contrary, the output cone disks 6 and 7 are rotatably engaged with the main shaft 10 by the ball spline 11 so that the input cone disks 4 and 5 can be rotated on the main shaft 10 by the bearing 51 in a stroke impossible state. The idea of the present invention can be applied to a toroidal type continuously variable transmission supported by the same concept.
[0068]
  Also above3rd to 6thIn the embodiment, a radial oil groove is formed on one side surface of the flange portion 52a that comes into contact with the end face of the input cone disk 5 (4) at the axial limit position of the tubular stopper 52, and at the axial limit position of the tubular stopper 52. A radial oil groove may be formed on the other side surface of the flange portion 52a that abuts against the end surface of the output cone disk 7 (6). If the radial oil groove is formed in this way, an oil flow radially outward from the ball spline 11 and the bearing 51 can be generated regardless of the axial limit position of the tubular stopper 52. The presence of the flange 52a does not cause poor lubrication or cooling of the bearing 51 or the ball spline 11.
[0069]
  Also above3rd to 6thThe shape of the tubular stopper 52 in the embodiment is not limited to that in the above embodiment, and may be, for example, a shape in which a flange 52a is provided near the center with respect to the axial direction of the tubular stopper 52. In the above embodiment, a coil spring or a specially shaped leaf spring is applied as the elastic body. However, the number of coil springs 54 and the shape of the leaf spring are not limited to those of the above embodiment, and are appropriately determined. Of course, it can be changed.
[Brief description of the drawings]
FIG. 1 of the present inventionOf a reference exampleIt is a principal part vertical side view which shows the toroidal type continuously variable transmission which becomes embodiment.
FIG. 2 is a cross-sectional view showing the toroidal-type continuously variable transmission as viewed in the direction of the arrow along the line AA in FIG.
FIG. 3 is an enlarged cross-sectional view showing details of a structure for retaining a bearing and a ball in a rear side toroidal transmission unit of the toroidal continuously variable transmission.
FIG. 4 shows the first aspect of the present invention.1FIG. 3 is a view similar to FIG. 3 showing a main part of the toroidal type continuously variable transmission according to the embodiment;
  (A) is a partially enlarged sectional view showing the upper half portion in a state when the tubular stopper is at one axial limit position;
  (B) is the elements on larger scale which show the lower half part in the state when a tubular stopper exists in the other axial direction limit position.
FIG. 5 shows the first of the present invention.2FIG. 3 is a view similar to FIG. 3 showing a main part of the toroidal type continuously variable transmission according to the embodiment;
  (A) is a partially enlarged sectional view showing the upper half portion in a state when the tubular stopper is at one axial limit position;
  (B) is the elements on larger scale which show the lower half part in the state when a tubular stopper exists in the other axial direction limit position.
6 is a front view showing the tubular stopper in the same embodiment as viewed in the axial direction from the right side of FIGS. 5 (a) and 5 (b). FIG.
FIG. 7 shows the first of the present invention.3It is a principal part vertical side view which shows the toroidal type continuously variable transmission which becomes embodiment.
FIG. 8 is a partially enlarged cross-sectional view showing details of a main part of the toroidal continuously variable transmission and a structure for preventing a coil spring, a bearing and a ball from coming off in the rear side toroidal transmission unit;
FIG. 9 is a partial enlarged cross-sectional view showing a main part of a modified example of the toroidal-type continuously variable transmission according to the embodiment.
FIG. 10 shows the first of the present invention.4It is a partial expanded sectional view which shows the principal part of the toroidal type continuously variable transmission which becomes embodiment.
FIG. 11 is a partially enlarged cross-sectional view showing a main part of a modified example of the toroidal-type continuously variable transmission according to the embodiment.
FIG. 12 shows the first of the present invention.5It is a partial expanded sectional view which shows the principal part of the toroidal type continuously variable transmission which becomes embodiment.
FIG. 13 shows the first of the present invention.6It is a partial expanded sectional view which shows the principal part of the toroidal type continuously variable transmission which becomes embodiment.
FIG. 14 is a partially enlarged cross-sectional view showing a main part of a modified example of the toroidal-type continuously variable transmission according to the embodiment.
FIG. 15 is a partially enlarged cross-sectional view showing a main part of a further modification of the toroidal-type continuously variable transmission according to the embodiment.

Claims (13)

A pair of discs are fitted on the main shaft, one of the discs is rotatably engaged on the main shaft, and the other disc is not strokeable on the main shaft and is supported rotatably by a bearing. In the toroidal type continuously variable transmission in which power is transferred between the disks by a power roller sandwiched between
A tubular stopper is tightly fitted on the main shaft so as to be displaceable in the axial direction by being disposed between the pair of discs, and the bearing is still used as the other disc even if the tubular stopper is displaced to the limit position in a direction away from the bearing. Determine the length of the tubular stopper so that it can continue to have a bearing stopper function to prevent it from slipping out ,
At least one of the axial limit positions of the tubular stopper is set by contact between a flange portion provided on the outer periphery of the tubular stopper so as to project between the pair of disks and a corresponding disk end surface. Toroidal-type continuously variable transmission. 2. The tubular stopper according to claim 1, wherein the tubular stopper also functions as a rotational engagement element stopper for preventing the rotational engagement element for rotationally engaging the one disk on the main shaft so as to be able to stroke from the one disk. A toroidal continuously variable transmission characterized by that.   3. The deformation of the disk according to claim 1 or 2 between the outer peripheral surface of at least one end of the tubular stopper entering the central hole of the disk and the inner peripheral surface of the corresponding disk. A toroidal continuously variable transmission characterized in that a clearance is set so that the inner peripheral surface of the disk does not interfere with the outer peripheral surface of the end of the tubular stopper. The toroidal continuously variable transmission according to any one of claims 1 to 3 , wherein a radial oil groove is formed on a surface of the flange portion that abuts against the end surface of the disk. A pair of discs are fitted on the main shaft, one of the discs is rotatably engaged on the main shaft, and the other disc is not strokeable on the main shaft and is supported rotatably by a bearing. In the toroidal type continuously variable transmission in which power is transferred between the disks by a power roller sandwiched between
A tubular stopper is tightly fitted on the main shaft so as to be displaceable in the axial direction by being disposed between the pair of disks, and between an inner peripheral surface of at least one of the pair of disks and an outer peripheral surface of the tubular stopper. Set a gap between
A toroidal continuously variable transmission, wherein an elastic body is interposed between the bearing and the tubular stopper. A pair of discs are fitted on the main shaft, and one of the discs can be rotated on the main shaft by a rotary engagement element, and the other disc can be stroked on the main shaft and can be rotated by a bearing. In a toroidal continuously variable transmission that supports and delivers power between the disks by a power roller clamped between the disks,
The gap between the inner peripheral surface of the disk stopper and the outer peripheral surface of the tubular stopper is set between the pair of disks and tightly fitted so that the tubular stopper can be displaced in the axial direction on the main shaft.
A toroidal continuously variable transmission characterized in that an elastic body is interposed between the rotary engaging element and the tubular stopper. A pair of discs are fitted on the main shaft, and one disc can be rotated on the main shaft by a rotary engagement element, and the other disc is not strokeable on the main shaft and supported by a bearing to be rotatable. In the toroidal type continuously variable transmission in which power is transferred between the disks by a power roller sandwiched between the disks,
The gap between the inner peripheral surface of the disk stopper and the outer peripheral surface of the tubular stopper is set between the pair of disks and tightly fitted so that the tubular stopper can be displaced in the axial direction on the main shaft.
A toroidal continuously variable transmission characterized in that an elastic body is interposed between a tip of the one disk or the other disk and the tubular stopper. A pair of discs are fitted on the main shaft, and one disc can be rotated on the main shaft by a rotary engagement element, and the other disc is not strokeable on the main shaft and supported by a bearing to be rotatable. In the toroidal type continuously variable transmission in which power is transferred between the disks by a power roller sandwiched between the disks,
The gap between the inner peripheral surface of the disk stopper and the outer peripheral surface of the tubular stopper is set between the pair of disks and tightly fitted so that the tubular stopper can be displaced in the axial direction on the main shaft.
A toroidal continuously variable transmission characterized in that an elastic body is interposed between the main shaft and the tubular stopper. A pair of discs are fitted on the main shaft, and one of the discs is rotatably engaged on the main shaft by a rotary engagement element, and the other disc is not strokeable on the main shaft and is supported rotatably by a bearing. In the toroidal type continuously variable transmission in which power is transferred between the disks by a power roller sandwiched between the disks,
The gap between the inner peripheral surface of the disk stopper and the outer peripheral surface of the tubular stopper is set between the pair of disks and tightly fitted so that the tubular stopper can be displaced in the axial direction on the main shaft.
A toroidal continuously variable transmission characterized in that an elastic body is interposed between the inner peripheral surface of the one disk or the other disk and the tubular stopper. 10. The toroidal continuously variable transmission according to claim 9 , wherein an inner diameter portion of the one disc or the other disc with the elastic body interposed therebetween has a stepped shape. In any one of Claims 5 thru | or 9 ,
A toroidal continuously variable transmission, characterized in that a bearing is provided between at least one end of the elastic body and the tubular stopper or between the other end of the elastic body and a member in contact therewith. In any one of Claims 5 thru | or 9 ,
A toroidal continuously variable transmission, wherein a lubricity improving member is provided between at least one end of the elastic body and the tubular stopper or between the other end of the elastic body and a member in contact therewith. In any one of Claims 5 thru | or 9 ,
A toroidal-type continuously variable transmission characterized in that at least one of the tubular stopper disposed on one end side of the elastic body or a member disposed on the other end side is formed integrally with the elastic body.

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