JP2006283900A - Toroidal continuously variable transmission and continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a structure capable of accurately detecting the rotational speed of an input side disk without requiring troublesome processing.
The input side disk and a rotating shaft are coupled via a first carrier 20a constituting a planetary gear type transmission. And the to-be-detected part 43 for detecting a rotational speed is installed in the outer peripheral surface of the 1st connection board 34 which comprises this 1st carrier 20a. The detected portion 43 is a concave-convex portion 42 in which concave portions 40, 40 and convex portions 41, 41 are alternately provided in the circumferential direction. Such a concavo-convex portion 42 does not need to be directly provided on the input side disk having high hardness, and can be easily processed. Further, since the first carrier 20a rotates in synchronization with the input side disk, the rotational speed can be accurately detected.
[Selection] Figure 1

Description

  The toroidal type continuously variable transmission and continuously variable transmission according to the present invention are used as an automatic transmission for automobiles or as a transmission for adjusting the operating speed of various industrial machines such as pumps.

  A toroidal continuously variable transmission is known as a type of transmission that constitutes a transmission for an automobile, and is partially implemented. Also, a continuously variable transmission that combines a toroidal-type continuously variable transmission and a planetary gear type transmission that is a gear-type differential unit is described in Patent Document 1 and the like, and various types have been conventionally known. 6 to 7 show the continuously variable transmission described in Patent Document 1. FIG. This continuously variable transmission is composed of a combination of a toroidal type continuously variable transmission 1 and first to third planetary gear type transmissions 2 to 4, and is supported concentrically and relatively rotatably. An input shaft 5, a rotation shaft 6, a transmission shaft 7, and an output shaft 8 are included.

  Among these, the toroidal type continuously variable transmission 1 includes a pair of input side disks 9a and 9b, each of which is a first disk and an outer disk, and an integrated output side which is a second disk and an inner disk. A disk 10 and a plurality of power rollers 11 and 11 are provided. These two input-side disks 9a and 9b are concentric with each other at two axially spaced positions on the rotary shaft 6 with one axial side surface having an arcuate cross section facing each other. In addition, the synchronous rotation is supported freely. Further, the output side disk 10 is arranged between the input side disks 9a, 9b around the intermediate portion of the rotary shaft 6 at both sides in the axial direction having a circular arc cross section. In a state of being opposed to one axial side surface of 9b, it is supported concentrically with both the input side disks 9a and 9b and relatively rotatable with respect to both the input side disks 9a and 9b. Further, a plurality of each of the power rollers 11 and 11 is sandwiched between both axial side surfaces of the output side disk 10 and one axial side surface of the both input side disks 9a and 9b. Transmission of power from the input side disks 9a and 9b to the output side disk 10 is made free.

  The power rollers 11 and 11 are rotatably supported on inner surfaces of trunnions 12 and 12 as support members described in the claims, and are provided at both ends of the trunnions 12 and 12, respectively. The pivots 13 and 13 are supported by the support plates 14a and 14b so as to be swingable and axially displaceable. Further, both the support plates 14 a and 14 b are supported by support posts 16 a and 16 b fixed in the casing 15. Further, both end portions in the axial direction of the output side disk 10 are rotatably supported by the support posts 16a and 16b by a pair of thrust angular ball bearings 17 and 17, respectively. Further, the output side disk 10 is spline-engaged with the base end portion (left end portion in FIG. 6) of the hollow rotary shaft 18, and the hollow rotary shaft 18 is connected to the input side on the side far from the engine (right side in FIG. 6). The rotational force of the output side disk 10 can be taken out by being inserted inside the disk 9b. Further, a first sun gear for constituting the first planetary gear type transmission 2 in a portion protruding from the outer surface of the input side disk 9b at the tip end portion (the right end portion in FIG. 6) of the hollow rotary shaft 18. A gear 19 is fixed.

  On the other hand, a first portion corresponding to the carrier described in the claims is provided between a portion protruding from the hollow rotary shaft 18 at the tip end portion (right end portion in FIG. 6) of the rotary shaft 6 and the input side disk 9b. The input disk 9b and the rotary shaft 6 are rotated in synchronism with each other by providing the carrier 20 therebetween. The first and second planetary gear type transmissions are respectively double pinion type at circumferentially equidistant positions (generally 3 to 4 positions) on both side surfaces in the axial direction of the first carrier 20. The planetary gears 21 to 23 for constituting 2, 3 are rotatably supported. Further, the first ring gear 24 is rotatably supported around one half (the right half in FIG. 6) of the first carrier 20, and at the base end (the left end in FIG. 6) of the transmission shaft 7. The second sun gear 25 for constituting the second planetary gear type transmission 3 is fixed.

  A second carrier 26 for constituting the third planetary gear type transmission 4 is coupled and fixed to a base end portion (left end portion in FIG. 6) of the output shaft 8. The second carrier 26 and the first ring gear 24 are coupled via a low speed clutch 27. In addition, a second ring gear 29 is disposed around a third sun gear 28 fixed to a portion near the tip of the transmission shaft 7 (near the right end in FIG. 6). A high speed clutch 30 is provided between the second ring gear 29 and a fixed portion of the casing 15 or the like. Further, a plurality of planetary gears 31 and 32 disposed between the second ring gear 29 and the third sun gear 28 are rotatably supported on the second carrier 26.

  In the case of the continuously variable transmission configured as described above, it is transmitted from the input shaft 5 to the integrated output side disk 10 via the rotating shaft 6, the pair of input side disks 9 a and 9 b, and the power rollers 11 and 11. Power is taken out through the hollow rotary shaft 18. In the low speed mode in which the low speed clutch 27 is connected and the high speed clutch 30 is disconnected, the rotational speed of the input shaft 5 is kept constant by changing the gear ratio of the toroidal continuously variable transmission 1. In this state, the rotational speed of the output shaft 8 can be freely converted into forward rotation and reverse rotation with the stop state interposed therebetween. That is, in this state, the output shaft 8 can be stopped by setting the gear ratio of the toroidal continuously variable transmission 1 to a predetermined value (GN point), and the gear ratio of the toroidal continuously variable transmission 1 can be stopped. Is changed from the predetermined value to the speed increasing side or the speed reducing side, the output shaft 8 is rotated in the direction of moving the vehicle backward or forward. Further, in the high speed mode in which the low speed clutch 27 is disconnected and the high speed clutch 30 is connected, the output shaft 8 is controlled by changing the gear ratio of the toroidal type continuously variable transmission 1 to the speed increasing side. The vehicle is rotated in the direction of moving forward.

  As described above, a desired gear ratio can be realized when the toroidal continuously variable transmission 1 is implemented, including the case where the continuously variable transmission is configured in combination with the planetary gear type transmissions 2, 3, and 4. It is necessary to feed back to the controller for gear ratio control. For this purpose, for example, it is conceivable to detect the tilt angle of the power rollers 11 and 11 with a potentiometer and perform gear ratio control according to the tilt angle (corresponding gear ratio). However, the use of the potentiometer in the toroidal type continuously variable transmission 1 mounted on an actual vehicle is not preferable because it not only increases the cost but also makes it difficult to ensure reliability. For this reason, the gear ratio is calculated from the ratio between the rotational speed of the input side disks 9a and 9b and the rotational speed of the output side disk 10.

  For example, in Patent Document 2, as a structure for detecting the rotational speed of the input side disk, an uneven portion for detecting the rotational speed is formed integrally with the input side disk on the outer peripheral edge of the input side disk. The invention has been described. However, in the case of such a structure described in Patent Document 2, since the uneven portion is formed on the outer peripheral edge portion of the hard disk on the input side, the processing of the uneven portion may be troublesome. The concave and convex portions for detecting the rotational speed are formed on the outer peripheral surface of an annular member (annular member), and the annular member is externally fixed to the outer peripheral surface of the input side disk by an interference fit. It is also conceivable to join the disc and the annular member together. With this configuration, it is not necessary to form the uneven portion on a member having high hardness such as the input side disk, so that the uneven portion can be easily processed. However, in this case, when the annular member is press-fitted into the outer peripheral surface of the input-side disk, the inner surface of the input-side disk (in contact with the peripheral surface of the power roller in rolling contact) The transmission traction surface) is likely to be damaged, such as scratches, and the shape accuracy, dimensional accuracy, surface roughness, etc. may not be maintained at a high level. Further, the press-fitting work performed while preventing such damage may lead to an increase in manufacturing cost, such as being troublesome and requiring skill.

  On the other hand, Patent Documents 3 to 4 provide a detected portion for detecting the rotational speed on the outer peripheral surface of a cage for holding a cam plate and a cam roller of a loading cam type pressing device. Is described as a rotational speed of the input side disk. In the case of such an invention, since it is not necessary to form irregularities on the input side disk, the processing can be facilitated. However, in the case of the loading cam type pressing device as described above, the meshing position of the cam roller changes with a change in pressing force (change in transmission power), and the cam plate and cam roller are changed based on the change in the meshing position. Rotates relative to the input disk. For this reason, based on this relative rotation, the actual rotational speed of the input side disk and the rotational speed of the cam plate and the cage detected as the rotational speed of the input side disk are slightly different. Produce.

  Patent Document 4 describes that such a deviation is canceled by an arithmetic unit. However, immediately after the cam plate or cage and the input disk start to rotate relative to each other, or when the relative rotation is abrupt, the actual rotation speed of the input disk and the rotation speed of the input disk The rotational speeds of the cam plate and the cage detected as can not be completely matched. For this reason, for example, when the torque passing through the toroidal-type continuously variable transmission is reversed or suddenly fluctuates based on the engine brake or the like, the rotational speed of the input-side disk, and thus this rotational speed. It is inevitable that the gear ratio calculated based on the above will deviate from the actual rotational speed or gear ratio. When the gear ratio is shifted in this way, the gear ratio control of the toroidal-type continuously variable transmission cannot be performed strictly, and the vehicle may be excessively accelerated or decelerated. Such inconvenience is not only when the continuously variable transmission is configured by the toroidal continuously variable transmission alone, but also when the toroidal continuously variable transmission is combined with a planetary gear transmission that is a differential unit. Also occurs.

  Moreover, in the case of the continuously variable transmission as shown in FIGS. 6 to 7, the output shaft 8 is stopped (geared neutral state) while the input shaft 5 is rotated in one direction. It is necessary to strictly regulate the gear ratio of the continuously variable transmission 1 to a predetermined value (GN point). At the same time, when the mode is switched from the low speed mode to the high speed mode, or conversely, from the high speed mode to the low speed mode, it is also necessary to strictly regulate the gear ratio to a predetermined value (mode switching point). However, if the actual rotational speed or gear ratio deviates from the detected or calculated rotational speed or gear ratio as described above, the gear ratio of the toroidal continuously variable transmission 1 cannot be strictly regulated. If the deviation is significant, the engine is stopped (engine stalled) in a geared neutral state, or the switching shock becomes large when the mode is switched.

JP 2004- 211744 A JP 2002-48205 A JP 11-63137 A JP 2000-55175 A

  The present invention has been invented to realize a structure capable of accurately detecting the rotational speed of the first disk (outer disk) without requiring troublesome processing or assembly work in view of the above-described circumstances. It is.

Of the toroidal type continuously variable transmission and continuously variable transmission of the present invention, the toroidal type continuously variable transmission according to claim 1 is the same as the conventional toroidal type continuously variable transmission, Each disk includes a second disk, a plurality of support members, and a plurality of power rollers.
Of these, the first and second discs are supported concentrically and independently of each other, with their inner surfaces facing each other, each having an arcuate cross section.
Each of the support members is freely provided with a swing displacement about a pivot that is twisted with respect to the center axis of each of the first and second disks.
Each of the power rollers is rotatably supported by the support members, and the circumferential surfaces of the spherical convex surfaces are in rolling contact with the inner surfaces of the first and second disks.
In particular, in the toroidal-type continuously variable transmission according to the first aspect of the present invention, the detected portion for detecting the rotation of the first disk is a member other than the first disk, and the first disk It is installed on a member that rotates in synchronization with the disk.

Of the toroidal continuously variable transmission and continuously variable transmission of the present invention, the toroidal continuously variable transmission according to claim 2 is a conventionally known toroidal as shown in FIGS. Similar to the type continuously variable transmission, the rotary shaft includes a pair of outer disks each serving as a first disk, an inner disk serving as a second disk, a plurality of support members, and a plurality of power rollers.
Among these, the rotating shaft is rotatably supported in the casing.
In addition, the both outer disks are arranged at two positions separated from each other in the axial direction among the rotating shafts in a state where the axial side surfaces of each of the outer circular disks face each other. Synchronized rotation is supported freely.
In addition, the inner disk has a relative to the rotating shaft in a state in which both axial side surfaces each having an arc cross section are opposed to one axial side surface of each outer disk around the intermediate portion of the rotating shaft. Rotation is supported freely.
The supporting members are pivoted in a twisted position with respect to the rotating shaft, each in a plurality of positions between both axial side surfaces of the inner disk and one axial side surface of the outer disk with respect to the axial direction. Oscillating displacement around the center is freely provided.
Further, each of the power rollers is rotatably supported by each of the supporting members, and each circumferential surface having a spherical convex surface is brought into rolling contact with both axial side surfaces of the inner disk and one axial side surface of each outer disk. I am letting.
In particular, in the toroidal-type continuously variable transmission according to the second aspect of the present invention, the detected portion for detecting the rotation of each of the outer disks is a member other than the outer disks, and the outer parts It is installed on a member that rotates in synchronization with the disk.

According to a sixth aspect of the present invention, the continuously variable transmission of the present invention includes a toroidal continuously variable transmission and a gear type differential unit (for example, a planetary gear type transmission) formed by combining a plurality of gears. The differential unit includes a first input unit (for example, a carrier) that is rotationally driven by an input shaft together with a first disk (a pair of outer disks) that constitutes the toroidal-type continuously variable transmission. It has a second input part (for example, a sun gear) connected to the disk (inner disk), extracts the rotation according to the speed difference between these first and second input parts, and transmits it to the output shaft To do.
In particular, in the continuously variable transmission of the present invention, the toroidal continuously variable transmission is a toroidal continuously variable transmission as described above.

According to the toroidal-type continuously variable transmission and continuously variable transmission of the present invention configured as described above, the rotational speed of the first disk (each outer disk) can be increased without requiring troublesome processing or assembly work. It can be detected accurately.
That is, in order to install the detected portion for detecting the rotation of the first disk (each outer disk) on a member that rotates in synchronization with the first disk (each outer disk), for example, a loading cam type Unlike the case where the detected portion is provided on a member that rotates relative to the first disk (each outer disk) such as a cam plate or a cam roller holder constituting the pressing device, the detected rotational speed is the actual rotational speed. There is no deviation. For this reason, the rotational speed of the first disk (each outer disk) and hence the gear ratio calculated from this rotational speed can always be obtained accurately, and the gear ratio control of the toroidal continuously variable transmission can be strictly performed. Yes. Moreover, in order to install the detected portion on a member other than the first disk (member other than the outer disks), for example, an uneven portion for detecting rotation is provided on the outer peripheral surface of the first disk (outer disk). There is no need for troublesome processing and assembly work, such as when directly forming or when an annular member provided with an uneven portion is fitted and fixed to the outer peripheral surface of the first disk (outer disk).

  When implementing the toroidal type continuously variable transmission of the present invention described in claims 1 and 2, preferably the carrier constituting the planetary gear type transmission which is a differential unit as described in claim 3, Rotation synchronized with the first disk is provided freely (more specifically, one outer disk of the pair of outer disks, which is the first disk, and the rotating shaft are connected to a planetary gear type transmission, which is a differential unit. Combined through the carrier constituting the machine). And a to-be-detected part is installed in this carrier (the part which does not overlap with a ring gear in a radial direction on the outer peripheral surface). In this case, for example, the detected part is an uneven part in which concave parts and convex parts are alternately provided in the circumferential direction, whereby the N pole and the S pole of the permanent magnet are alternately provided in the circumferential direction. Or by forming slit-shaped through-holes at equal intervals in the circumferential direction to make an encoder in which the magnetic characteristics are changed alternately and at equal intervals in the circumferential direction. it can. For example, when the detected portion is an uneven portion, the uneven portion is formed directly on the outer peripheral surface of the carrier, and the uneven portion is formed on the outer peripheral surface of an annular member (annular member). Such an annular member can also be externally fixed to the outer peripheral surface of the carrier by interference fitting, adhesion, welding, or the like.

  If configured in this way, the uneven part for detecting rotation is directly formed on the first disk (outer disk), or the annular member provided with such an uneven part is externally fixed to the first disk. It does not require troublesome processing and assembly work. In other words, the carrier, which is a member that rotates in synchronization with the first disk, does not transmit power in rolling contact with each power roller, unlike the first disk. For this reason, it is not necessary to ensure the hardness of the carrier as much as the first disk. Therefore, when the uneven portion for detecting rotation is formed on the outer peripheral surface of the carrier, the uneven portion can be easily formed. In addition, when the annular member, the encoder, and the like are externally fitted and fixed to the outer peripheral surface of the carrier, it is not necessary to protect the traction surface, unlike when the annular member is press-fitted to the first disk. . For this reason, these annular members, encoders and carriers can be easily assembled.

  In addition, when providing an uneven part directly on the outer peripheral surface of the carrier, the uneven part is not only used as an uneven part for detecting rotation, but also as an uneven part for transmitting rotational force between the first disk and the carrier. Can be used. That is, a plurality of (for example, four) engaging projections are provided on the side surface of the first disk at equal intervals in the circumferential direction, and the projections and depressions provided on the carrier are provided with these engaging projections. The concave and convex portions are engaged with a part of a plurality of constituent concave portions (several times the engaging convex portions, for example, 16). And by such uneven | corrugated engagement, while these 1st discs and a carrier are couple | bonded so that rotational force can be transmitted, rotation detection is performed by the uneven | corrugated | grooved part of the said carrier. In such a case, it is not necessary to separately form the engaging portion between the first disk and the carrier and the detected portion for detecting the rotation of the first disk, so that further processing work can be simplified. And manufacturing cost can be reduced.

  Further, when the toroidal continuously variable transmission according to the present invention described in claims 1 and 2 is implemented, preferably, as described in claim 4, the first disk (each A hydraulic pressing device that presses the outer disk toward the second disk (inner disk) is provided. Then, the cylinder constituting the pressing device is provided to freely rotate in synchronization with the first disk, and the detected portion is installed in the cylinder. In this case, the detected portion can employ a concavo-convex portion or the like, similarly to the structure described in claim 3 described above. Of course, an annular member provided with such an uneven portion or the like can be externally fixed to the cylinder.

  Even in this configuration, the rotational speed of the first disk (outer disk) can be accurately detected without the need for troublesome processing and assembly work, as in the structure described in claim 3 above. Moreover, since the cylinder constituting the pressing device constitutes the hydraulic chamber, the axial dimension is increased to some extent. For this reason, the degree of freedom of the installation position of the detected portion can be increased by the increase in the axial dimension. Further, when the annular member provided with the uneven portion is externally fixed to the outer peripheral surface of the cylinder, the annular member can prevent oil leakage of the pressing device. That is, when the hydraulic pressure in the hydraulic chamber of the pressing device rises, even if the opening edge of the cylinder tends to expand on the basis of the hydraulic pressure, the annular member fitted and fixed to the cylinder increases the diameter. suppress. For this reason, it is possible to prevent oil leakage at the sliding contact portion between the inner peripheral surface of the cylinder based on such an enlarged diameter and the outer peripheral surface of the piston (including the first disk). The pressure drop can be prevented. As a result, it is possible to prevent slippage at the rolling contact portion (traction portion), to reduce the size of the pump for introducing the pressure oil into the pressing device, and to prevent a decrease in transmission efficiency.

  Further, when the toroidal continuously variable transmission according to the present invention described in claims 1 and 2 is implemented, preferably, as described in claim 5, the first disk (each outer disk) is synchronized. The rotating member is an input shaft for inputting power from the engine to the first disk, or a driven member that is rotationally driven by a drive gear provided on the input shaft. The detected portion is the unevenness of the driving gear or the unevenness of the driven gear that is provided on the driven member and meshes with the driving gear.

  Even in such a configuration, the rotational speed of the first disk (outer disk) can be accurately adjusted without the need for troublesome processing and assembling work, similarly to the structure described in claims 3 and 4 described above. Can be detected. In addition, the toroidal continuously variable transmission has a driven shaft and an input shaft of the hydraulic pump for driving a hydraulic pump for feeding the pressure oil to a portion requiring pressure oil such as a control valve and a pressing device. Must be connected via gears. And when the unevenness of the gear provided on the driven shaft or the input shaft is used as a detected portion for detecting rotation, the detected portion for detecting the rotational speed of the outer disk in other portions. This eliminates the need to provide a work piece, further simplifies processing operations, and reduces manufacturing costs.

Preferably, when the continuously variable transmission of the present invention described in claim 6 is implemented, the toroidal continuously variable transmission and the differential unit are connected via a clutch device as described in claim 7. In addition, the transmission state of power can be switched based on the connection / disconnection of the clutch device. In addition, as described in claim 8, the input shaft is unidirectionally adjusted by adjusting the gear ratio of the toroidal type continuously variable transmission to change the relative displacement speeds of the plurality of gears constituting the differential unit. The rotation state of the output shaft can be converted into normal rotation and reverse rotation with the stopped state in the rotated state.
In such a configuration, in order to strictly control the gear ratio of the toroidal-type continuously variable transmission, it is necessary to accurately detect the rotational speed of the outer disk. Therefore, the significance of carrying out the present invention with the structure as described above becomes large.

  FIG. 1 shows Embodiment 1 of the present invention corresponding to claims 1, 2, 3, 6, 7 and 8. The feature of this embodiment is that a pair of input side disks 9a and 9b (see FIG. 6), each of which is the first disk and the outer disk, are used without requiring troublesome processing and assembly work. The point is to accurately detect the rotation speed. The structure of the toroidal continuously variable transmission 1 incorporating these respective input side disks 9a and 9b, and the structure of the continuously variable transmission incorporating this toroidal continuously variable transmission 1 are shown in FIGS. Since it is the same as the conventional structure described, the illustration and detailed description will be omitted or simplified, and the following description will focus on the features of the present invention.

  Also in the case of the present embodiment, as in the conventional structure shown in FIGS. 6 to 7, one of the pair of input side disks 9a and 9b (right side in FIG. 6) and the rotating shaft 6 Are coupled via a first carrier 20a constituting the first and second planetary gear type transmissions 2 and 3 (see FIG. 6) which are differential units. That is, the first carrier 20a shown in detail in FIG. 1 is provided in a state of being spanned between the tip end portion (right end portion in FIG. 6) of the rotating shaft 6 and the one input side disk 9b. The first carrier 20a includes an intermediate support plate 33 and first and second connection plates 34 and 35. The intermediate support plate 33 and the first and second connection plates 34 and 35 are connected to a connecting portion 55, respectively. , 55 connected to each other. Also, a plurality of planetary shafts 36 and 37 (see FIG. 6) are provided between the intermediate support plate 33 and the first and second connecting plates 34 and 35, respectively (three in the illustrated example). A plurality of (three in the illustrated example) planetary shafts 38 (see FIG. 6) are spanned between the first and second connecting plates 34, 35, respectively. Further, around the planetary shafts 36 to 38, planetary gears 21, 22, and 23 (see FIG. 6) are rotatably supported.

  The cylindrical portion 56 provided at the center of the intermediate support plate 39 is spline-engageable with a portion near the tip of the intermediate portion of the rotating shaft 6. Then, the first carrier 20a is held on the rotary shaft 6 by holding the cylindrical portion 56 with a loading nut 39 (see FIG. 6) in a state where the cylindrical portion 56 and the rotary shaft 6 are in spline engagement. , It is coupled so that the rotational force can be transmitted (synchronized rotation can be freely performed). Further, a portion of the outer peripheral surface of the first carrier 20a that does not overlap in the radial direction with the first ring gear 24 (see FIG. 6) in the assembled state, that is, the first connecting plate 34 constituting the first carrier 20a. A detected portion 43 for detecting the rotation of the first carrier 20a is provided on the outer peripheral surface.

  In the case of the present embodiment, the detected portion 43 is an uneven portion 42 in which the concave portions 40 and 40 and the convex portions 41 and 41 are alternately provided in the circumferential direction. That is, the concave portions 40 and 40 (projecting in the radial direction) are radially recessed from the outer peripheral surface at a plurality of circumferentially equidistant locations (16 locations in this example) on the outer peripheral surface of the first connecting plate 34. By forming the convex portions 41, 41) directly in this state, the concave and convex portion 42 that becomes the detected portion 43 is configured. In such a concavo-convex portion 42, detection of one or more rotation sensors (not shown) supported on a fixed portion such as the casing 15 (see FIG. 6) in a state where the first carrier 20a is assembled to the continuously variable transmission. Make the parts close to each other. As such a rotation sensor, a magnetic type, a capacitance type, an eddy current type, or the like can be adopted. Since the first carrier 20a is made of a metal having magnetism and conductivity, such as carbon steel, various magnetic properties, capacitance characteristics, and the like of the outer peripheral surface of the first connecting plate 34 constituting the first carrier 20a. The characteristics change alternately and at equal intervals in the circumferential direction based on the unevenness of the uneven portion 42. Accordingly, by selecting an appropriate structure as the rotation sensor, the rotation speed of the first carrier 20a, and hence the input side disks 9a and 9b rotating in synchronization with the first carrier 20a can be determined. Accurately required.

  In the case of the present embodiment, the uneven portion 42 is used not only as an uneven portion for detecting rotation but also as an uneven portion for transmitting rotational force between the one input side disk 9b and the first carrier 20a. To do. For this purpose, a plurality of (for example, four) engaging projections 44 (for example, four) are provided on the outer side surface (the right side surface in FIG. 6) of the one input side disk 9b with the circumferentially spaced apart ones. 6). Then, by engaging these engaging convex portions 44 with the concave portions 40, 40 provided at positions that align with the engaging convex portions 44 in the concave and convex portions 42 of the first carrier 20a. The one input side disk 9b and the first carrier 20a are coupled so as to transmit a rotational force. In the case of the present embodiment, rotation detection is performed as described above by the unevenness of the uneven portion 42 of the first carrier 20a. For this reason, the number of the engaging projections 44 provided on the outer surface of the one input side disk 9b can sufficiently transmit power between the first carrier 20a and the one input side disk 9b, and The number is such that the rotation can be detected with a required accuracy even in a state where each of the engaging convex portions 44 and the concave and convex portions 42 are engaged. In addition, in order to prevent each said engagement convex part 44 engaged with any one of the recessed parts 40 and 40 from interfering with rotation detection, each recessed part 40 and 40 engaged with these each engagement convex part 44 is shown. It is also possible to increase the depth in the radial direction and engage the engagement protrusions 44 with the back portions of the recesses 40, 40.

  In the case of the present embodiment as described above, the rotational speeds of the respective input side disks 9a and 9b can be accurately detected without requiring troublesome processing. That is, the first carrier 20a, which is a member that rotates in synchronization with the input side disks 9a and 9b, rolls with the power rollers 11 and 11 (see FIG. 7) such as the input side disks 9a and 9b. It does not contact and transmit power. For this reason, it is not necessary to secure the hardness of the first carrier 20a as much as the input disks 9a, 9b. Therefore, it is possible to easily perform the operation of forming the uneven portion 42 for detecting rotation on the outer peripheral surface of the first carrier 20a. Moreover, the first carrier 20a formed with the concavo-convex portion 42 does not rotate relative to the input side disks 9a and 9b, such as a cam plate or a cam roller holder constituting a loading cam type pressing device. Absent. For this reason, the rotational speed of each of the input side disks 9a and 9b, and hence the gear ratio calculated from the rotational speed, can always be obtained accurately, and the gear ratio control of the toroidal continuously variable transmission can be performed strictly. The

  In the case of the present embodiment, as described above, the uneven portion 42 for detecting rotation is also used as an uneven portion for connecting one input side disk 9b and the first carrier 20a. For this reason, it is not necessary to separately make an engagement portion between the one input side disk 9b and the first carrier 20a and a detected portion for detecting the rotation of the input side disk 9b. Further processing work can be simplified and manufacturing costs can be reduced.

  Further, the first carrier 20a is less displaced in the axial direction during operation. That is, the amount of axial displacement during operation of the first carrier 20a is the amount accompanying the elastic deformation of the input side disk 9b and the power rollers 11 and 11 on the first carrier 20a side. On the other hand, for example, the axial displacement amount of the cylinder 46 of the pressing device as shown in FIGS. 2 to 4 described later and FIG. In addition to the above, the extension of the rotating shaft 6 is also added, so that it becomes larger than the axial displacement of the first carrier 20a. As in this embodiment, when the first carrier 20a having a small amount of axial displacement is provided with the uneven portion 42, which is the detected portion 43, the amount of deviation in the axial direction between the uneven portion 42 and the rotation sensor is also reduced. Less. For this reason, even if the width dimension in the axial direction of the concavo-convex portion 42 is limited, it is possible to easily ensure the rotation accuracy.

  In addition, although illustration is omitted, it becomes a detected portion by forming bottomed circular holes at a plurality of circumferentially equidistant positions on the outer peripheral surface of the first carrier (the first connecting plate constituting the first carrier). An uneven portion can also be formed. In this case, each said circular hole becomes each recessed part, and the part between adjacent circular holes in the said outer peripheral surface becomes each convex part. Further, by replacing the detected portion 43 with the uneven portion 42 as described above, by fitting an annular permanent magnet in which the N poles and S poles of the permanent magnet are alternately arranged in the circumferential direction, The magnetic characteristics of the partial outer peripheral surface of the first carrier may be changed alternately and at equal intervals over the circumferential direction.

  Further, for example, as disclosed in Japanese Patent Application No. 2004-50958 and the like, a wave-type encoder in which small-diameter portions and large-diameter portions are alternately arranged in the circumferential direction, or conventionally known. Any encoder can be used as long as the magnetic characteristics are changed alternately and at equal intervals in the circumferential direction. When such a structure is adopted, such an encoder or an annular member provided with this encoder is tightly fitted to the outer peripheral surface of the first connecting plate 34 constituting the first carrier 20a, and is bonded and welded. Fix by external fitting. In this way, when the encoder and the annular member are fitted and fixed to the first carrier 20a, the traction as in the case where such an encoder and the annular member are fitted and fixed to the outer peripheral surfaces of the input side disks 9a and 9b is used. There is no need to protect the surface. For this reason, the assembly work of these annular members and encoders can be easily performed.

  FIG. 2 shows a second embodiment of the present invention corresponding to claims 1, 2, and 4. In the case of the present embodiment as well, as in the conventional structure shown in FIGS. 6 to 7 described above, a double piston type that presses the other input side disk 9a toward one input side disk 9b as the hydraulic pressure is fed. The hydraulic pressing device 45 is provided. Then, among the constituent members of the pressing device 45, the rotation synchronized with the rotating shaft 6 is achieved by being coupled and fixed to the proximal end portion of the rotating shaft 6 (the left end portion in FIGS. 2 and 6) with an interference fit. A detected portion 43a for detecting the rotation of the cylinder 46 is provided on the outer peripheral surface of the cylinder 46 provided freely. In the case of the present embodiment, the detected portion 43a is a concavo-convex portion 42a in which the concave portions 40a and 40a and the convex portions 41a and 41a are provided alternately at equal intervals over the circumferential direction. That is, the concave and convex portions serving as the detected portion 43a are formed by directly forming a plurality of concave portions 40, 40 in a state where the outer peripheral surface of the cylinder 46 is radially recessed from the outer peripheral surface. Part 42a is configured.

In this embodiment as well, as in the first embodiment, the rotational speeds of the input disks 9a and 9b can be accurately detected without the need for troublesome processing. Moreover, since the cylinder 46 constituting the pressing device 45 constitutes the hydraulic chamber 47 (see FIG. 6), the axial dimension is increased to some extent. For this reason, as the axial dimension increases, the axial dimension of the detected portion 43a is easily secured, and the degree of freedom of the installation position can be increased.
Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted.

  3 to 4 show a third embodiment of the present invention corresponding to claims 1, 2, and 4. FIG. In the case of the present embodiment as well, the detected portion 43b for detecting the rotation of the cylinder 46 is installed on the outer peripheral surface of the cylinder 46 constituting the pressing device 45 (see FIG. 6), as in the second embodiment. is doing. However, in the case of the above-described second embodiment, the uneven portion 42a that becomes the detected portion 43a is formed directly on the outer peripheral surface of the cylinder 46, whereas in the case of the present embodiment, the detected portion 43b The uneven | corrugated | grooved part 42b which becomes is formed in the outer peripheral surface of the annular member 48 which is a ring-shaped member. That is, in the case of the present embodiment, the concave portions 40b and 40b and the convex portions 41b and 41b constituting the concave and convex portion 43b are alternately provided on the outer peripheral surface of the annular member 48 in the circumferential direction. Such an annular member 48 is fitted and fixed to the outer peripheral surface of the cylinder 46 from the state shown in FIG. 4 to the state shown in FIG. The cylinder 46 is integrally connected.

In the case of this embodiment as well, as in Embodiments 1 and 2, the rotational speeds of the input side disks 9a and 9b (see FIG. 6) are reduced without requiring troublesome processing and assembly work. It can be detected accurately. That is, the operation of fitting and fixing the annular member 48 to the cylinder 46 can be performed without taking protection of the traction surface. For this reason, this operation can be easily performed. In addition, in the case of the present embodiment, oil leakage of the pressing device 45 can be prevented by externally fitting the annular member 48 provided with the uneven portion 43b to the cylinder 46. That is, when the hydraulic pressure in the hydraulic chamber 47 of the pressing device 45 is increased (even though the diameter of the piston 49 (see FIG. 6) of the pressing device 45 is different, the pressure increases to about 0.4 to 0.8 MP), Even if the opening edge of the cylinder 46 tends to expand on the basis of this hydraulic pressure, the annular member 48 suppresses the expansion. For this reason, it is possible to prevent oil from leaking at the sliding contact portion between the inner peripheral surface of the cylinder 46 and the outer peripheral surface of the piston 49 based on such an enlarged diameter, and the pressing force of the pressing device 45 based on the oil leak is reduced. Decline can be prevented. As a result, it is possible to prevent slippage at the rolling contact portion, to reduce the size of the hydraulic pump for introducing pressure oil into the pressing device 45, and to prevent a decrease in transmission efficiency.
Other configurations and operations are the same as those of the first and second embodiments described above, and a duplicate description is omitted.

  FIG. 5 shows a fourth embodiment of the present invention corresponding to claims 1, 2, and 5. In the case of the present embodiment, the unevenness of the drive gear 50 fixed on the outer peripheral surface of the intermediate portion of the input shaft 5 is used as the detected portion 43b for detecting rotation. That is, as shown in FIG. 6 described above, the closing member 51 that closes the opening on the side (left side in FIG. 6) where the engine is provided in the casing 15 (see FIG. 6) constituting the continuously variable transmission is as follows. In addition to rotatably supporting the input shaft 5, as shown in detail in FIG. 5, a hydraulic pump 52 such as a gear pump that is driven based on the rotation of the input shaft 5 is incorporated. The hydraulic pump 52 is for feeding pressure oil to a portion requiring pressure oil, such as the gear ratio control valve of the toroidal type continuously variable transmission 1 or the pressing device 45 (see FIG. 6). Then, in order to rotationally drive the hydraulic pump 52 by the input shaft 5, the drive gear 50 is fixed to the input shaft 5 (even if it is formed integrally with the input shaft 5, it is separated from the input shaft 5. The driven gear 54 is fixed to the driven shaft 53 of the hydraulic pump 52, and the driven gear 50 and the driven gear 54 are engaged with each other. In the case of the present embodiment, a rotation sensor is brought close to and opposed to the outer peripheral surface (tooth surface) of the drive gear 50 out of the gears 50 and 54, whereby the drive gear 50, further the input shaft 5, The rotational speeds of the input side disks 9a and 9b (see FIG. 6) that rotate in synchronization with the shaft 5 can be detected. Instead of the drive gear 50, the rotation of the driven gear 54 may be detected. Of these driving gears 50 and driven gears 54, it is preferable from the viewpoint of ensuring the stability of rotational speed detection to detect the rotation of a gear having a small axial displacement during operation.

  In the case of this embodiment as well, the rotational speeds of the input side disks 9a and 9b can be accurately detected without the need for troublesome processing and assembly work as in the first to third embodiments. Moreover, the toroidal-type continuously variable transmission 1 is driven by the hydraulic pump 52 for feeding the pressure oil to the parts requiring the pressure oil such as the transmission ratio control valve and the pressing device 45 as described above. It is necessary to connect the driven shaft 53 of the hydraulic pump 52 and the input shaft 5 via gears 50 and 54, respectively. In the case of this embodiment, in which the unevenness of the gears 50 and 54 is used as a detected portion 43b for detecting rotation, the rotational speed of each of the input side disks 9a and 9b is detected in other portions. This eliminates the need to provide the detected portion, further simplifies the processing work, and reduces the manufacturing cost. Other configurations and operations are the same as those in the first to third embodiments, and thus a duplicate description is omitted.

  The present invention can be carried out regardless of whether the type of toroidal continuously variable transmission is a double cavity type or a single cavity type, and whether it is a half toroidal type or a full toroidal type. . In addition, various configurations including a conventionally known configuration such as a rotation sensor for detecting a rotation speed and a detected portion can be adopted.

The principal part perspective view which shows Example 1 of this invention. The principal part perspective view which shows the same Example 2. FIG. The principal part perspective view which shows the same Example 3. FIG. The perspective view similar to FIG. 3 which shows the state before a cylinder and an annular member are assembled | attached. The principal part perspective view which shows Example 4 of this invention in the state seen from the back back surface (back side right side of paper surface) of FIG. Sectional drawing which shows an example of the continuously variable transmission incorporating the toroidal type continuously variable transmission conventionally known. AA sectional drawing of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Toroidal type continuously variable transmission 2 1st planetary gear type transmission 3 2nd planetary gear type transmission 4 3rd planetary gear type transmission 5 Input shaft 6 Rotating shaft 7 Transmission shaft 8 Output shaft 9a, 9b Input side disk 10 Output side disk 11 Power roller 12 Trunnion 13 Axis 14a, 14b Support plate 15 Casing 16a, 16b Support post 17 Ball bearing 18 Hollow rotary shaft 19 First sun gear 20, 20a First carrier 21 Planetary gear 22 Planetary gear 23 Planetary gear 24 First ring gear 25 Second sun gear 26 Second carrier 27 Low speed clutch 28 Third sun gear 29 Second ring gear 30 High speed clutch 31 Planetary gear 32 Planetary gear 33 Intermediate support plate 34 First connection plate 35 Second connection Plate 36 Planetary axis 37 Planetary axis 38 Planetary axis 39 Loading nut 40, 40a, 4 b Concave part 41, 41a, 41b Convex part 42, 42a, 42b Concave part 43, 43a, 43b Detected part 44 Engaging convex part 45 Pressing device 46 Cylinder 47 Hydraulic chamber 48 Annular member 49 Piston 50 Drive gear 51 Closing member 52 Hydraulic pressure Pump 53 Driven shaft 54 Driven gear 55 Connecting part 56 Cylindrical part

Claims (8)

  The first and second discs are concentrically and rotatably supported independently of each other, each having an arc-shaped cross section facing each other, and the central axes of these discs. A plurality of support members that are provided with a freely oscillating displacement centering on the pivot at the position of twisting, and each peripheral surface that is rotatably supported by each of these support members and has a spherical convex surface In the toroidal-type continuously variable transmission including a plurality of power rollers that are in rolling contact with the inner surface of each second disk, the detected part for detecting the rotation of the first disk is the first part. A toroidal continuously variable transmission characterized in that it is installed on a member that rotates in synchronization with the first disk, other than the disk.   The first disk is in two axially separated positions among the rotation shafts rotatably supported in the casing, with each axial side surface having a circular arc cross section facing each other. A pair of outer disks supported to freely rotate in synchronization with the rotation shaft, and the second disk has axially opposite side surfaces each having an arc cross section around the intermediate portion of the rotation shaft. An inner disk that is supported to freely rotate relative to the rotating shaft in a state of being opposed to one axial side surface of each outer disk. Each of the power rollers is provided with a plurality of oscillating displacements around a pivot that is twisted with respect to the rotating shaft, and a plurality of each of the power rollers is disposed between one axial side surface of the outer disk. For supporting member Each peripheral surface that is supported in a freely rolling manner and has a spherical convex surface is in rolling contact with both axial side surfaces of the inner disk and one axial side surface of each outer disk, and detects the rotation of each outer disk. The toroidal-type continuously variable transmission according to claim 1, wherein the detected portion is installed on a member that rotates in synchronization with each outer disk by a member other than these outer disks.   The carrier which comprises the planetary gear type transmission which is a differential unit is freely provided to rotate in synchronization with the first disk, and the detected portion is installed on this carrier. A toroidal-type continuously variable transmission according to claim 1.   A hydraulic pressing device is provided that presses the first disk toward the second disk as the pressure oil is fed, and a cylinder constituting the pressing device is freely provided to rotate in synchronization with the first disk. The toroidal continuously variable transmission according to any one of claims 1 to 2, wherein a detected portion is installed in the cylinder.   The member that rotates in synchronization with the first disk is an input shaft for inputting power from the engine to the first disk, or a driven member that is rotationally driven by a drive gear provided on the input shaft. 3. The detection unit according to claim 1, wherein the detected portion is an unevenness of the driving gear or an unevenness of the driven gear that is provided on the driven member and meshes with the driving gear. Toroidal continuously variable transmission.   A toroidal-type continuously variable transmission and a gear-type differential unit formed by combining a plurality of gears. Among these units, the differential unit is coupled with an input shaft together with a first disk constituting the toroidal-type continuously variable transmission. It has a first input unit that is rotationally driven and a second input unit that is also connected to the second disk, and takes out rotation according to the speed difference between the first and second input units. In the continuously variable transmission that transmits to the output shaft, the toroidal continuously variable transmission is the toroidal continuously variable transmission according to any one of claims 1 to 5. A continuously variable transmission characterized by the above.   The continuously variable transmission according to claim 6, wherein the toroidal continuously variable transmission and the differential unit are connected via a clutch device, and the transmission state of power can be switched based on the connection and disconnection of the clutch device. By adjusting the gear ratio of the toroidal-type continuously variable transmission and changing the relative displacement speed of the gears that make up the differential unit, the output shaft rotates while the input shaft rotates in one direction. The continuously variable transmission according to any one of claims 6 to 7, wherein the transmission is convertible into forward rotation and reverse rotation with the stop state interposed therebetween.

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