CN100460715C - Ring CVT - Google Patents

Abstract

Prevent the power rollers (4, 7) from tilting excessively. Protrusions (66, 66) are provided on respective stop members (73, 73) fixed to both ends of the trunnions (30, 31). Further, recesses (67, 67) are provided on inner surfaces of end plates (48, 48) constituting the swing frames (21, 22) at positions facing the respective protrusions (66, 66). And, the respective protrusions (66, 66) are inserted into the respective recesses (67, 67) so as to be displaceable with respect to the swing direction of the respective trunnions (30, 31). In addition, at the same time, by making the side surfaces of the above-mentioned convex parts (66, 66) abut against the inner surfaces of the above-mentioned concave parts (67, 67) according to the swinging of these trunnions (30, 31), the Each of these trunnions (30, 31) swings above a predetermined level.

Description

Ring CVT

technical field

The toroidal continuously variable transmission according to the present invention is used, for example, as a transmission unit constituting an automatic transmission for a vehicle (automobile).

Background technique

As a transmission for automobiles, toroidal continuously variable transmissions have been studied, and some of them have been implemented. As for passenger vehicles, for example, a large-scale and large-scale torque-generating transmission described in Patent Document 1 is conventionally known. The structure of the engine is suitable as a transmission unit of an automatic transmission for a four-wheel drive vehicle. 5 to 8 show a toroidal continuously variable transmission for a large-displacement four-wheel-drive vehicle described in Patent Document 1. As shown in FIG. The toroidal continuously variable transmission 1 is respectively provided with three first power rollers 4, 4 between the first input side disc 2 and the first output side disc 3, and between the second input side disc 5 and the second output side Three second power rollers 7 are provided between the disks 6 , and power is transmitted through a total of six power rollers 4 and 7 .

In order to constitute the above-mentioned automatic transmission device, a torque converter 8 as a starting clutch is provided at the frontmost part in the transmission direction of power, and the output part of the torque converter 8 is assembled with the ring-shaped stepless The front half 9 a of the input shaft 9 of the transmission 1 . The front half 9 a is rotationally driven by the torque converter 8 described above as a running engine (not shown) rotates. Further, the rear half 9b of the input shaft 9 is supported concentrically with each other and relatively rotatable on the rear end portion of the front half 9a.

Further, between the front half 9a and the rear half 9b, a forward and backward switching means 10 for switching forward and backward is provided in series with respect to the power transmission direction. The forward/backward switching unit 10 as a planetary gear mechanism switches between a forward state and a reverse state by selectively disconnecting and connecting a forward clutch 11 and a reverse clutch 12 which are wet multi-plate clutches.

Regarding the transmission direction of power, the toroidal continuously variable transmission 1 is provided on the rear side of the forward-backward switching unit 10 as described above. And the input part of this toroidal continuously variable transmission 1, that is, the part connected to the output part of the above-mentioned forward and backward switching unit 10, and the output part, that is, connected to the drive shaft 13 for the front wheel and the drive shaft 14 for the rear wheel The gear ratio between the upper parts changes continuously. This toroidal continuously variable transmission 1 is provided around the rear half portion 9b. That is, in the vicinity of the front and rear ends of the rear half 9b, the first and second two sides are supported concentrically and rotatably in synchronization with each other in a state where the inner surfaces, which are concave surfaces each having an arc-shaped cross section, face each other. Enter the side plates 2,5. For this reason, in the illustrated example, the first input side plate 2 provided on the front side (the left side in FIG. Block forward movement. On the other hand, the second input side plate 5 provided on the rear side (the right side in FIG. 5 ) is supported by the rear end portion of the rear half 9 b via the ball spline 16 . Furthermore, the second input side disk 5 is freely pressed toward the first input side disk 2 by a hydraulic loading device 17 .

Moreover, the support cylinder 18 is provided concentrically with the said rear half part 9b around the intermediate part of the said rear half part 9b. Both ends of the support cylinder 18 are supported and fixed by the inner diameter side ends of the struts 19 , 19 . In addition, these struts 19, 19 support and fix their respective outer diameter side ends to support rings 20, 20 to be described later, and are configured to freely support first and second swing frames 21, which will also be described later. , 22, first and second supporting frames 23,24. In addition, the rear half 9b is supported inside the support tube 18 and the first and second output side disks 3 and 6 are supported around the support tube 18 so as to be rotatable and axially displaceable, respectively. In addition, the two output side disks 3 and 6 support an axial load applied therebetween via a thrust bearing provided therebetween, and freely perform mutual relative rotation.

In addition, the output gear 25 for the front wheels is fixed to the outer side of the first output side disk 3, and the output gear 25 for the front wheels is engaged with the drive shaft 13 for the front wheels via the driven gear 26 for the front wheels. , the front wheel drive shaft 13 is freely rotatably driven by the first output side disc 3 . Further, the rotation of the drive shaft 13 for the front wheels is freely transmitted to the front wheels (not shown) via the differential gear 27 for the front wheels. On the other hand, the output gear 28 for the rear wheels is fixed on the outer side of the second output side disk 6, and the output gear 28 for the rear wheels is engaged with the drive shaft 14 for the rear wheels via the driven gear 29 for the rear wheels. Together, the above-mentioned rear wheel drive shaft 14 is freely rotatably driven by the above-mentioned second output side disc 6 . Further, the rotation of the drive shaft 14 for the rear wheels is freely transmitted to the rear wheels (not shown) via the differential gear for the rear wheels (not shown).

In addition, the above-mentioned three first power rollers 4, 4 are sandwiched between the inner surface of the above-mentioned first input side disk 2 and the inner surface of the above-mentioned first output side disk 3, and the above-mentioned three second power rollers 7 It is sandwiched between the inner surface of the second input side disk 5 and the inner surface of the second output side disk 6 . The first and second power rollers 4 and 7 are rotatably supported by the inner surfaces of the first and second trunnions 30 and 31 on the respective displacement shafts 32 and 32 protruding from the inner surfaces. around. These first and second trunnions 30, 31 do not intersect with the central axes of the above-mentioned discs 2, 5, 3, 6 which are concentrically arranged on their respective two ends, but exist in relation to these The first and second pivots 33 (the second pivots are not shown) are pivoted at positions where the central axes of the disks 2, 5, 3, and 6 are twisted at right angles or close to the right angles. In addition, the above-mentioned first and second trunnions 30 and 31 are supported on both ends of the first and second swing frames 21 and 22 so as to be able to swing and displace freely.

And, the intermediate portions of the above-mentioned first and second swing frames 21 and 22 are supported between the above-mentioned support rings 20 and 20 constituting the above-mentioned first and second support frames 23 and 24 so as to be opposite to each other. The support shafts 34, 34 provided in a direction parallel to or nearly parallel to the central axes of the respective disks 2, 5, 3, 6 are centered to freely swing and displace. The first and second support frames 23 , 24 are formed by connecting each pair of support rings 20 , 20 arranged in parallel to each other through the outer diameter side ends of the three support portions 35 , 35 constituting the support 19 . become. The support shafts 34, 34 are erected on each of the support frames 23, 24 constituting the first and second support frames 23, 24 at the intermediate positions of the support rings 20, 20 in the middle position of the support rings 20, 20. The pair of support rings 20, 20 are located between each other. Therefore, the first and second swing frames 21 and 22 are swingably supported between the pillar portions 35 and 35 adjacent to each other in the circumferential direction.

Furthermore, the above-mentioned first and second swing frames 21, 22 are freely moved under the action of hydraulic cylinders 36a, 36b provided between the two ends of these swing frames 21, 22 and the above-mentioned support rings 20, 20. ground swing displacement. These respective hydraulic cylinders 36a, 36b are respectively provided at positions where a part of each of the support rings 20, 20 is matched with both end portions of the respective swing frames 21, 22 described above. On the other hand, the rods 37a, 37b are parallel to the support shafts 34, 34 through both ends of the first and second swing frames 21, 22 so as to penetrate through the first and second swing frames 21, 22, and so on. The state of both ends of 22 is supported and fixed on the parts matched with the above-mentioned hydraulic cylinders 36a, 36b. Then, the pistons 38a, 38b fitted in the respective hydraulic cylinders 36a, 36b are engaged with the respective rods 37a, 37b. When shifting, two pairs are provided on each of the above-mentioned swing frames 21, 22 (4 pairs are provided on each swing frame, and a total of 24 pairs are provided as the toroidal continuously variable transmission 1 as a whole) Among the hydraulic cylinders 36a, 36b, one hydraulic cylinder 36a (36b) provided on one end side in the longitudinal direction of each of the above-mentioned swing frames 21, 22 is extended, and the other hydraulic cylinder 36b (36a) is contracted, The respective swing frames 21 and 22 are made to swing and displace by a predetermined amount in a predetermined direction.

In addition, a control valve 39 for controlling supply and discharge of pressurized oil to each of the above-mentioned hydraulic cylinders 36a, 36b is supported on each of the above-mentioned support rings 20, 20. When the above-mentioned swing frames 21, 22 are swing-displaced by the supply and discharge of pressure oil to the above-mentioned hydraulic cylinders 36a, 36b, the outer surfaces of the trunnions 30, 31 supported on these swing frames 21, 22 The upper cam surface 40 displaces the spool 42 of the control valve 39 via the plunger 41 attached to the control valve 39 to switch the control valve 39 . The sleeve 43 constituting the control valve 39 together with the spool 42 is displaced to a predetermined position in advance under the action of the control motor 44, so that the desired gear ratio can be achieved during gear shifting. Such a control valve 39 and a control motor 44 are provided one on the side of the first cavity 45 composed of the above-mentioned first input side disk 2 and the first output side disk 3, and one is provided on the side including the above-mentioned second input side disk 5 and the first output side disk 3. There is one second cavity 46 formed by two output side disks 6 , and two are provided in the entire toroidal continuously variable transmission 1 . And, according to the instruction signal from the not shown controller that has built-in microcomputer, by the control motor 44 of the first chamber 45 side, to the control valve 39 of the first chamber 45 side, by the second chamber 46 side, The control motor 44 of the control valve 39 on the side of the second cavity 46 is controlled synchronously (in the case of a straight-forward state) or independently (in the case of a rotating state).

Due to this configuration, during gear shifting, the first and second swing frames 21, 22 move around the support shafts 34, 34 in accordance with the supply and discharge of pressure oil to the hydraulic cylinders 36a, 36b. A given amount of oscillating displacement in a given direction. As a result, the first and second trunnions 30 , 31 supported by these swing frames 21 , 22 perform arcuate motion (rotational motion) around the support shafts 34 , 34 . And, by the axial displacement of the first and second trunnions 30 and 31 with respect to the first and second pivot shafts 33 based on the arc motion, The orientation of the force in the tangential direction on the rolling contact portion (traction portion) between the surface and the inner surface of each of the disks 2 , 5 , 3 , 6 is changed. And, as the direction of the force changes, the first and second trunnions 30, 31 are pivotally supported by the first and second pivots 33 on the first and second swing frames 21, 22. The center swings in opposite directions to each other, the contact positions between the peripheral surfaces of the above-mentioned first and second power rollers 4, 7 and the above-mentioned inner surfaces change, and the first and second input side discs 2, 5 and the first and second The rotational speed ratio between the second output side disks 3, 6 varies.

During operation of the conventional toroidal continuously variable transmission 1 configured as described above, the first and second input-side disks 2, 5 that rotate synchronously with the rear half 9b of the input shaft 9 rotate through the first The power transmitted from the input side disk 2 to the first output side disk 3 via the first power rollers 4 and 4 is used to rotationally drive the front wheel drive shaft 13 . In addition, the rear wheel drive shaft 14 is rotationally driven by power transmitted from the second input side disk 5 to the second output side disk 6 via the respective second power rollers 7 .

In the case of the toroidal continuously variable transmission as described above, when the torque passing through the toroidal continuously variable transmission fluctuates suddenly or when the gear ratio fluctuates suddenly, there is a possibility that the gear ratio exceeds a predetermined value and then converges to a predetermined value. value overshoot. And, if such an overshoot occurs in a state where the first and second power rollers 4 and 7 are greatly inclined (a state where the transmission ratio of the toroidal continuously variable transmission is largely deviated from 1), these power rollers 4 , 7 may be excessively inclined and easily make the peripheral surfaces of these power rollers 4, 7 reach the end edges of the first, second input side, and output side discs 2, 5, 3, 6. That is, the contact ellipse formed on the rolling contact portion (traction portion) of the peripheral surface of each of the above-mentioned power rollers 4, 7 and the inner surface of each of the above-mentioned disks 2, 5, 3, 6 is easy to ride on these respective disks 2, 5, 6 On the end edges of 3 and 6, damage due to edge loads tends to occur on these respective power rollers 4 and 7 and the respective disks 2, 5, 3 and 6. Such damage is not preferable because the durability of the power rollers 4, 7 and the discs 2, 5, 3, 6 will be reduced.

For example, as described in Patent Document 2, in the case of a structure in which a trunnion supporting a power roller is supported on a support plate supported by a case, excessive swinging of the trunnion is restricted by providing on the support plate or the like. The abutment part can prevent the trunnion and the above-mentioned power roller supported on the trunnion from being excessively tilted. However, in the structure shown in above-mentioned FIGS. In the case of the above-mentioned patent document 2, each trunnion is not supported by the support plate like the structure described in the said patent document 2. In addition, in the case of the structures shown in the above-mentioned FIGS. 5 to 8 , the space for installing the above-mentioned mating member is limited, and the structure described in the above-mentioned Patent Document 2 cannot be adopted as it is.

In addition, when the torque passing through the toroidal continuously variable transmission fluctuates suddenly as described above, there is a possibility that jumping occurs in which the gear ratio does not converge to a predetermined value due to overshooting. Such jumping is not preferable because it reduces the drivability (running stability) in addition to reducing the transmission efficiency and increasing the vibration.

Patent Document 1: JP-A-2001-165262

Patent Document 2: Shikaihei No. 6-43404

Contents of the invention

The toroidal continuously variable transmission of the present invention was invented in view of the above-mentioned circumstances, in order to prevent the power roller from inclining excessively, and to realize a structure having good durability.

The toroidal continuously variable transmission of the present invention includes an input side disk and an output side disk, a plurality of trunnions, and a plurality of power rollers.

Among them, the input-side disk and the output-side disk are rotatably supported concentrically and independently of each other in a state where inner surfaces, which are concave surfaces each having an arc-shaped cross section, face each other.

In addition, each of the trunnions swings around a pivot axis at a position twisted with respect to the central axis of the input-side disk and the output-side disk.

In addition, each of the power rollers has a spherical convex surface and is sandwiched between the input-side disk and the output-side disk while being supported on the respective trunnions.

In addition, the same number of swing frames as the number of each trunnion, which pivotally support each intermediate portion on the support frame provided around each of the trunnions via the support shaft, can be freely displaced by the actuator. In addition, at the same time, the respective pivots provided at both ends of the respective trunnions are swingably supported on both ends of the respective swing frames.

In particular, in the toroidal continuously variable transmission of the present invention, a swing restricting mechanism for preventing the swing of the trunnions above a predetermined limit is provided between the swing frames and the trunnions.

According to the toroidal continuously variable transmission of the present invention constituted as described above, the swing restricting mechanism provided between each swing frame and each trunnion can prevent these trunnions and the power rollers supported on these trunnions from being overwhelmed. tilted. That is, even in the state where the respective power rollers are greatly inclined (the state where the gear ratio of the toroidal continuously variable transmission deviates greatly from 1), overshoot may occur in which the gear ratio exceeds a predetermined value and then converges to a predetermined value. There is a tendency that the trunnions supporting the power rollers are also restricted from excessive swinging by the swinging restricting mechanism. Therefore, the contact ellipse formed on the rolling contact portion (traction portion) between the peripheral surface of each power roller supported on these respective trunnions and the inner surface of each disk does not ride on the end edges of these disks. The durability of these power rollers and disks is ensured.

Description of drawings

Fig. 1 is a cross-sectional view of main parts showing Embodiment 1 of the present invention.

FIG. 2 is a view along the arrow A with a part omitted.

Fig. 3 is that the surface of the stop member facing the end surface of the trunnion is the upper side in Fig. 3 (A), and the surface opposite to the inner surface of the end plate is the upper side in Fig. 3 (B), Stereoscopic views of the respective representations.

FIG. 4 is a diagram similar to FIG. 2 showing Embodiment 2 of the present invention.

Fig. 5 is a cross-sectional view showing an example of a conventional structure.

Fig. 6 is a B-B sectional view of Fig. 5 .

Fig. 7 is its C-C sectional view.

8 is a cross-sectional view showing substantially the same parts as in FIG. 7 cut along a plane including the central axis of the first pivot provided at both ends of the first trunnion.

Label description

1. Toroidal continuously variable transmission

2 The first input side panel

3 The first output side plate

4 The first power roller

5 Second input side panel

6 Second output side plate

7 Second Power Roller

8 torque converter

9 input shaft

9a first half

9b second half

10 forward and backward switching unit

11 forward clutch

12 Reverse clutch

13 Drive shaft for front wheel

14 Drive shaft for rear wheel

15 carrier

16 ball spline

17 Loading device

18 support cylinder

19 pillars

20 support ring

21 First swing frame

22 second swing frame

23 The first support frame

24 Second support frame

25 Output gear for front wheel

26 Driven gear for front wheel

27 Differential gear for front wheel

28 output gear for rear wheel

29 Driven gear for rear wheel

30 first trunnion

31 Second trunnion

32, 32a displacement axis

33 First Pivot

34 Support shaft

35 Pillar

36a, 36b hydraulic cylinder

37a, 37b rod

38a, 38b Piston

39 control valve

40 cam face

41 plunger

42 spool

43 sleeve

44 Control motor

45 First cavity

46 Second cavity

47 subject

48 end plate

49 threaded parts

50 support wall

51 round hole

52 Radial Needle Roller Bearings

53 Thrust needle roller bearing

54 outer ring

55 Pads

56 round holes

57 Large diameter part

58 Trail Department

59 Stairs

60 thrust ball bearing

61 outer ring

62 Radial Needle Roller Bearings

63 Thrust needle roller bearing

64 Radial Needle Roller Bearings

65 Swing limit mechanism

66 Convex

67 Concave

68 Recessed hole

69 Partition parts

70 Engagement recess

71 The first oil path

72 Second oil path

73 stop parts

74 disc part

75 locking protrusion

76 inner ring

77 elastic parts

Detailed ways

When carrying out the present invention, as described in claim 2, it is preferable that the swing restricting mechanism is constituted by a convex portion and a concave portion. These protrusions and recesses are provided on the end surfaces of the pivots provided on both ends of each trunnion and on the inner surfaces of the respective swing frames facing the end surfaces (between the end surfaces of the pivots and the inner surfaces of the swing frames). Either one of them can be provided with a convex portion or a concave portion). And, the above-mentioned convex part is inserted into the above-mentioned concave part in a state capable of being displaced (relatively displaced) with respect to the swinging direction of each of the above-mentioned trunnions. Furthermore, by bringing the side surfaces of the convex portions into contact with the inner surfaces of the concave portions in response to the swinging of the respective trunnions, these trunnions are prevented from swinging beyond a predetermined limit.

According to this configuration, it is possible to realize a structure capable of preventing excessive inclination of the trunnions and the power rollers supported by the trunnions simply and without enlarging the installation space.

In addition, when carrying out the invention described in Claim 2, preferably, as described in Claim 3, between the side surface of the convex portion and the inner surface of the concave portion, a resistance that resists the swinging of the trunnion is provided. The mechanism, in other words, is provided with a resistance mechanism (damping mechanism) that imparts an anti-vibration force (damping force) to the above-mentioned trunnion. For example, as described in Claim 4, the resistance mechanism has a structure in which lubricating oil introduced into the space formed by the side surface of the convex part and the inner surface of the concave part enters and exits from the space according to the displacement of the convex part. Alternatively, as described in claim 5, the resistance mechanism is configured by sandwiching an elastic member between the side surfaces of the convex portion and the inner surface of the concave portion that face each other.

If such a resistance mechanism (damping mechanism) is provided, it is possible to prevent the trunnions described above and the power rollers supported by the trunnions from being excessively inclined (vibrating unnecessarily). That is, even if there is a tendency for jumping in which the transmission ratio does not converge to a predetermined value due to sudden torque fluctuations, etc., the above-mentioned trunnions supporting the above-mentioned power rollers will be affected by the resistance mechanism constituting the above-mentioned resistance mechanism. Swing resistance objects (lubricating oil, elastic parts) prevent excessive swinging. Therefore, such bouncing is less likely to occur, and it is possible to prevent a decrease in transmission efficiency, an increase in vibration, and a decrease in running stability.

Example 1

1 to 3 show Embodiment 1 of the present invention corresponding to technical solutions 1 to 4. In addition, the present invention is characterized in that these (first , the second) durability of the power roller 4 (7) and (first, second) input side, each disc 2,5,3,6 (referring to FIG. 5 ) of the output side. The structures and functions of other parts are the same as those of the conventional structures shown in FIGS. 5 to 8 above, so repeated illustrations and descriptions are omitted or simplified. The structures and functions of the parts shown in FIGS. 1 to 3 will be described below. In addition, in the following description, "first" and "second" representing first and second members having different cavities are omitted.

Each swing frame 21 (22) supported on the support frame 23 (24) via the support shaft 34 (refer to FIGS. 5 to 8 ) is a pair of end plates 48, 48 combined and fixed in a substantially U-shaped shape by screws 49, 49. Formed on both ends of the main body 47. Inside the circular holes 51, 51 concentrically formed on a pair of support wall portions 50, 50 provided on both ends of the main body 47, only swingingly supported in a state where axial displacement is prevented. Pivot shafts 33, 33 are provided concentrically with each other at both end portions of the respective trunnions 30 (31). For this reason, in the case of the present embodiment, radial needle roller bearings 52, 52 and thrust rollers are provided between the inner peripheral surfaces of the above-mentioned round holes 51, 51 and the outer peripheral surfaces of the above-mentioned pivot shafts 33, 33. Needle bearings 53, 53.

And, in order to arrange these two needle roller bearings 52,53 concentrically, the outer peripheral surfaces of the outer rings 54,54 of these two needle roller bearings 52,53 and the gaskets embedded and fixed in the above-mentioned respective circular holes 51,51 The inner peripheral surface of 55,55 is spherically fitted. The above-mentioned two needle bearings 52, 53 are formed by arranging a plurality of them respectively between the above-mentioned outer rings 54, 54 having self-alignment properties and the inner rings 76, 76 fitted on the outer peripheral surfaces of the above-mentioned pivot shafts 33, 33. Made of needles.

As described above, only the intermediate portions of the above-mentioned trunnions 30 (31), which are supported on the above-mentioned respective swing frames 21 (22) in a swing-displaceable manner around the pivot shafts 33, 33, are freely swing-displaceable. The base half of the displacement shaft 32a is supported. For this reason, a circular hole 56 is formed in the middle portion of each of these trunnions 30 ( 31 ) so as to penetrate the inner and outer peripheral surfaces of each of these trunnions 30 ( 31 ). Each of these round holes 56 has a stepped shape in which the large-diameter portion 57 on the inner side of each trunnion 30 ( 31 ) and the small-diameter portion 58 on the outer side are continuous through a stepped portion 59 . And, in such a circular hole 56 , the displacement shaft 32 a integrally formed with the outer ring 61 constituting the angular contact type thrust ball bearing 60 is rotatably supported by a radial needle bearing 62 . In addition, a thrust needle bearing 63 is provided between the outer surface of the outer ring 61 and the inner surface of each of the trunnions 30 (31), so that the movement between the outer ring 61 and the outer ring 61 around the displacement shaft 32a can be smoothly performed. Displacement of power roller 4(7). Further, the power roller 4 ( 7 ) is rotatably supported around the front half of the displacement shaft 32 a by the thrust ball bearing 60 and another radial needle bearing 64 .

Furthermore, in the case of the present embodiment, a swing restricting mechanism is provided between each of the above-mentioned swing frames 21 (22) and each of the above-mentioned trunnions 30 (31) to prevent these trunnions 30 (31) from swinging more than predetermined. 65, 65. In the case of the present embodiment, each of these swing restricting mechanisms 65, 65 is composed of a pair of convex portions 66, 66 and a pair of concave portions 67, 67, respectively. That is, on the inner side surfaces of the above-mentioned end plates 48, 48 that are fixedly connected to the two ends of the above-mentioned swing frames 21 (22), and on the inner surfaces of the two ends of the above-mentioned trunnions 30 (31). Bottom-shaped concave hole portions 68 , 68 are provided on opposing portions of the end surfaces of the respective pivot shafts 33 , 33 in a state of being recessed from the inner surfaces. In addition, the above-mentioned recessed portions 67 , 67 having fan-shaped openings are respectively provided at two positions on the radially opposite sides of the respective recessed hole portions 68 , 68 .

For this reason, in the case of this embodiment, the partition members 69, 69 are fitted in the above-mentioned respective concave hole portions 68, 68 in a state in which the rotation in the respective concave hole portions 68, 68 is prevented. The portions surrounded by the side surfaces of the members 69 , 69 and the inner surfaces (inner peripheral surfaces and bottom surfaces) of the recessed hole portions 68 , 68 constitute the respective recessed portions 67 , 67 . The partition members 69 , 69 prevent movement in the circumferential direction of the respective recessed portions 68 , 68 in a state engaged with the engaging recessed portions 70 , 70 provided on the bottom surfaces of the respective recessed portions 68 , 68 . displacement. In addition, by fitting the outer peripheral surfaces of the partition members 69 , 69 into the inner peripheral surfaces of the concave holes 68 , 68 , displacement of the partition members 69 , 69 in the radial direction of the concave holes 68 , 68 is prevented. . In addition, at the center of each of these partition members 68, 68, there is provided a first oil passage for supplying lubricating oil to portions of the thrust ball bearing 60 and radial needle roller bearings 62, 64, etc. that require cooling and lubrication. 71, and on the radially outer side of the first oil passage 71, second oil passages 72, 72 for supplying and discharging lubricating oil to the above-mentioned recesses 67, 67 are provided.

On the other hand, on the end surfaces of the respective pivots 33, 33 provided on the both ends of the above-mentioned respective trunnions 30 (31), the above-mentioned recesses provided on the inner surfaces of the above-mentioned respective end plates 48, 48 are aligned with each other. An annular stopper member 73 is fixed at a position where the holes 68 and 68 face each other. As shown in FIG. 3 , the stopper member 73 is provided with the above-mentioned protrusions 66 , 66 and locking recesses 75 , 75 on both axial sides of the circular plate portion 74 in a state protruding in the axial direction from the respective sides. . Wherein each convex portion 66,66 is respectively arranged on the single side of the above-mentioned disc portion 74 (the lower side of FIG. 3(A), similarly, the upper side of FIG. 3(B), the outer side of FIG. The outer portion and the radially opposite sides of the circular plate portion 74 are located at two locations. In addition, the above-mentioned locking recesses 75, 75 are respectively provided on the other side of the above-mentioned circular plate portion 74 (the upper side of FIG. 3(A), similarly, the lower side of FIG. 3(B), and the inner side of FIG. 1 ). The radially inner portion is located at a position shifted by 90 degrees from the respective protrusions 66 , 66 with respect to the circumferential direction of the circular plate portion 74 .

And, by locking the locking recesses 75, 75 in the locking recesses (not shown) formed on the end surfaces of the pivot shafts 33, 33, the stopper member 73 is stopped relative to the trunnions. The state of relative rotation of 30 (31) is fixed on both ends of each of the above-mentioned trunnions 30 (31). In this state, the respective convex portions 66 , 66 are inserted into the respective concave portions 67 , 67 so as to be displaceable with respect to the swing direction of the respective trunnions 30 ( 31 ). In addition, at the same time, the side surfaces of the respective convex portions 66, 66 abut against the inner surfaces of the respective concave portions 67, 67 and the side surfaces of the partition members 69, 69 due to the swinging of the respective trunnions 30 (31). , to prevent these trunnions 30 (31) from swinging more than predetermined. In other words, in the state where the protrusions 66, 66 are inserted into the recesses 67, 67, the side surfaces of the protrusions 66, 66 are not in contact with the inner surfaces of the recesses 67, 67. Displacement of the aforementioned trunnion 30 ( 31 ) with respect to the swing direction. Therefore, by properly restricting the intervals between the respective convex portions 66, 66 from the side surfaces and the swinging of the inner surfaces of the concave portions 67, 67 by the respective trunnions 30 (31), the respective convex portions 66, 66 can be aligned with each other. The positional relationship between the side contact parts of these trunnions 30 (31) and the positional relationship in the swing direction of these trunnions 30 (31), and the above-mentioned power rollers supported on these trunnions 30 (31) can be 4(7) The tilt angle is limited to the desired range.

In the case of the present embodiment constituted as described above, the swing restricting mechanisms 65, 65 provided between each swing frame 21 (22) and each trunnion 30 (31), that is, the above-mentioned protrusions 66, 66 and each The recesses 67, 67 can prevent these trunnions 30 (31) and the power rollers 4 (7) supported on these trunnions 30 (31) from being excessively inclined. That is, in the state where the respective power rollers 4 (7) are greatly inclined (the state where the transmission ratio of the toroidal continuously variable transmission is largely deviated from 1), even if the transmission ratio exceeds a predetermined value and then converges to a predetermined value, The overshooting tendency of the above-mentioned each convex part 66, 66 can also be prevented from further swinging when the side surfaces of the above-mentioned respective convex parts 66, 66 abut against the inner surfaces of the above-mentioned concave parts 67, 67, that is, the side surfaces of the partition members 69, 69. Therefore, the rolling contact portions formed on the peripheral surfaces of the above-mentioned power rollers 4 (7) supported on these trunnions 30 (31) and the inner surfaces of the input side and output side discs 2, 5 (3, 6) The contact ellipse on the (traction part) can not ride on the edge of these each disc 2,5 (3,6), can ensure that these each power roller 4 (7) and each disc 2,5 (3,6) durability.

In addition, in the case of this embodiment, lubricating oil is sent into the space formed by the side surfaces of the respective convex portions 66, 66 and the inner surfaces of the concave portions 67, 67 through the second oil passages 72, 72. (The part indicated by the oblique grid in Figure 2). And, by filling the above-mentioned space with lubricating oil, a resistance mechanism as a resistance against the swing of each of the above-mentioned trunnions 30 (31) is constituted. That is, by filling the lubricating oil in the space in this way, when the respective protrusions 66, 66 are displaced as the respective trunnions 30 (31) swing, the lubricating oil is withdrawn from the respective protrusions 66, 66. The opening force (the force to return the lubricating oil to the second oil passage 72, 72, to make the lubricating oil pass through the inner diameter side and outer diameter side of each convex portion 66, 66 and the inner diameter of each concave portion 67, 67 the force of the gap between the surfaces).

Such a force acts as a force (anti-vibration force, shock-absorbing force) for preventing these trunnions 30 (31) from vibrating unnecessarily, via the stopper members 73, 73 provided with the above-mentioned respective convex portions 66, 66. Above-mentioned each trunnion 30 (31) on. Therefore, these respective trunnions 30 ( 31 ) and the respective power rollers 4 ( 7 ) supported on these respective trunnions 30 ( 31 ) can be prevented from being excessively inclined (vibrating unnecessarily). That is, even if there is a tendency that the gear ratio does not converge to a predetermined value due to sudden torque fluctuations, etc., the above-mentioned trunnions 30 (31) supporting the above-mentioned power rollers 4 (7) will prevent this by the above-mentioned force. swing excessively. Therefore, such bouncing is less likely to occur, and it is possible to prevent a decrease in transmission efficiency, an increase in vibration, and a decrease in running stability.

In addition, the force (vibration resistance, shock absorbing force) applied to each trunnion 30 (31) via each protrusion 66, 66 as described above can be adjusted by adjusting the inner diameter of the second oil passage 72, 72, each protrusion. The size of the gap between the radially inner and outer peripheral surfaces of the portions 66 , 66 and the inner surfaces of the recesses 67 , 67 can be limited to a desired value.

Example 2

Fig. 4 shows Embodiment 2 of the present invention corresponding to technical proposals 1-3, 5. In the case of the second embodiment, the side faces of the protrusions 66 and 66 provided on the stopper member 73 and the recesses 67 and 67 provided on the end plate 48 constituting the swing frame 21 (refer to FIG. 1 ) Elastic members 77, 77 are provided between the inner surfaces of the trunnions to constitute a resistance mechanism that acts as a resistance to the swing of the trunnion 30 (see FIG. 1 ). That is, by sandwiching the above-mentioned elastic members 77, 77 such as compression coil springs between the side surfaces of the above-mentioned respective convex portions 66, 66 facing each other and the inner surfaces of the above-mentioned concave portions 67, 67, these convex portions 66, The side surface of 66 and the inner surface of each recessed part 67, 67 apply force in the direction which mutually separates. Such a force is applied to each of the trunnions via the stopper member 73 provided with the protrusions 66 , 66 as a force (vibration resistance force, damping force) in a direction in which these trunnions 30 are prevented from vibrating unnecessarily. 30 on. In the case of this embodiment, since the above-mentioned elastic members 77, 77 are provided, the lubricating oil is not filled into the space formed by the inner surfaces of the convex portions 66, 66 and the concave portions 67, 67. Therefore, the second oil passages 72 , 72 (see FIG. 2 ) are not provided on the partition member 69 constituting the above-mentioned recessed portions 67 , 67 . The other structures and functions are the same as those of the above-mentioned embodiment 1, so repeated descriptions are omitted.

Although this invention was demonstrated in detail with reference to the specific embodiment, it is possible for those skilled in the art to add various changes and corrections without deviating from the mind and range of this invention.

This application is based on the JP Patent application (Japanese Patent Application No. 2004-198755) of an application on July 6, 2004, The content is referred and used here.

Claims (5)

1. A toroidal continuously variable transmission, comprising: An input-side disk and an output-side disk that are rotatably supported concentrically and independently of each other in a state where concave surfaces each having an arc-shaped cross section, that is, mutual inner surfaces face each other; a plurality of trunnions oscillating about a pivot in a twisted position relative to the central axis of the two discs; a plurality of power rollers that are sandwiched between the above two disks in a state of being supported on each of these trunnions and whose peripheral surfaces are spherical convex surfaces; and An actuator that freely supports the middle part of the swing frame on the support frame provided around the above-mentioned trunnions through the support shaft, and the number of the swing frames is the same as the number of the above-mentioned trunnions; Wherein, the above-mentioned pivots provided on the two ends of the above-mentioned trunnions are freely swingable supported on the two ends of the above-mentioned swing frames; It is characterized in that, Between each of the above-mentioned swing frames and each of the above-mentioned trunnions, there is provided a swing restricting mechanism for preventing these respective trunnions from swinging more than a predetermined value, and the above-mentioned swing restricting mechanism includes end faces of pivots provided on both ends of each of the trunnions. The convex portion on the top, and the concave portion on the inner surface of each swing frame facing these respective end surfaces. 2. The toroidal continuously variable transmission according to claim 1, wherein the convex portion is inserted into the concave portion so that the trunnions can be displaced in the swing direction, and by These trunnions are prevented from swinging by a predetermined amount or more by swinging so that the side surface of the above-mentioned convex portion abuts against the inner surface of the above-mentioned concave portion. 3. The toroidal continuously variable transmission according to claim 2, wherein a resistance mechanism for generating resistance to the swing of the trunnion is provided between the side surface of the convex portion and the inner surface of the concave portion. 4. The toroidal continuously variable transmission as claimed in claim 3, wherein the resistance mechanism has the function of causing the lubricating oil introduced into the space formed by the side surface of the convex portion and the inner surface of the concave portion to move from and to the space according to the displacement of the convex portion. The structure that the space enters and exits. 5. The toroidal continuously variable transmission according to claim 3, wherein the resistance mechanism is constituted by sandwiching an elastic member between the side surfaces of the convex portion and the inner surface of the concave portion opposed to each other.

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