JP2011064253A - Continuously variable transmission and assembling method of the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission and an assembling method of the continuously variable transmission which can improve workability when meshing a stepped planetary gear with two sun gears to assemble the continuously variable transmission. <P>SOLUTION: The continuously variable transmission consists of a toroidal type continuously variable transmission 1 and a planetary gear type transmission 2. Integrated gears 31, which are the stepped planetary gears, are formed to have the same shape, but two planetary gears 8 and 9 of the integrated gear 31, have a different number of teeth respectively. All integrated gears 31 have the same module. The integrated gears 31 are arranged on a carrier 7 at equal intervals. The total of the teeth of one planetary gear 8 of the two planetary gears 8 and 9, and a sun gear 15 meshing with the planetary gear 8, is equalized to the total of teeth of the other planetary gear 9 and a sun gear 11 meshing with the planetary gear 9. These values are multiples of the number of integrated gears 31 supported by the carrier 7. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a continuously variable transmission and a method for assembling a continuously variable transmission, which can be used in transmissions of automobiles and various industrial machines, and which are a combination of a toroidal type continuously variable transmission and a planetary gear type transmission.

2. Description of the Related Art Conventionally, it has been proposed to configure a continuously variable transmission by combining a toroidal continuously variable transmission and a planetary gear transmission as an automatic transmission for an automobile (see, for example, Patent Documents 1 and 2).
For example, in the example shown in Patent Document 1, as shown in FIG. 14, the continuously variable transmission is configured by combining a toroidal continuously variable transmission 1 and a planetary gear transmission 2. Of these, the toroidal continuously variable transmission 1 includes an input shaft 3 to which rotational torque is input, input-side disks 4 and 4 that are supported by the input shaft 3 and rotate integrally with the input shaft 3, and the input-side disk. The output side disk 5 to which the rotational torque is transmitted from the input side disks 4 and 4 with a changeable gear ratio via the power rollers 6 and 6 sandwiched between the power rollers 6 and 4, and the power rollers 6 and 6 And a pressing device that applies a pressing force in the axial direction to the input-side disks 4 and 4 and the output-side disk 5 in the sandwiched state. That is, the toroidal-type continuously variable transmission 1 includes input-side disks 4 and 4 and an output-side disk 5 that are supported concentrically and rotatably with their inner surfaces facing each other, and both of these disks. A plurality of power rollers 6, 6 sandwiched between 4, 5.

The planetary gear type transmission 2 includes a carrier 7 coupled and fixed to the input shaft 3 and one (on the right side in FIG. 14) input side disk 4. A first transmission shaft 10 having planetary gears 8 and 9 fixed to both ends is rotatably supported at the radial intermediate portion of the carrier 7. Further, on the opposite side of the input shaft 3 with the carrier 7 interposed therebetween, a second transmission shaft 13 having sun gears 11 and 12 fixed to both ends is rotatably supported while being concentric with the input shaft 3. ing. Then, the sun gear 15 is meshed with the planetary gear 8. The sun gear 15 is connected to the output side disk 5 at the base end portion (left end portion in FIG. 14). The right end of FIG. 14 is fixed.
Further, the planetary gear 9 is engaged with a sun gear 11 fixed to one end portion (left end portion in FIG. 14) of the second transmission shaft 13. One planetary gear 8 (on the left in FIG. 14) is meshed with a ring gear 17 that is rotatably provided around the carrier 7 via another planetary gear 16.

On the other hand, a second carrier 18 is disposed around the sun gear 12 fixed to the other end portion (the right end portion in FIG. 14) of the second transmission shaft 13, and the second carrier 18 includes a planetary gear 19, 20 is rotatably supported. The second carrier 18 is fixed to the proximal end portion (left end portion in FIG. 14) of the output shaft 21 that is disposed concentrically with the input shaft 3 and the second transmission shaft 13. The planetary gears 19 and 20 mesh with each other, and one planetary gear 19 is provided in the sun gear 12 and the other planetary gear 20 is provided around the second carrier 18 so as to be rotatable. 22 are engaged with each other.
In addition, the ring gear 17 and the second carrier 18 can be engaged and disengaged by a low speed clutch 23, and the second ring gear 22 and a fixed part such as a housing can be engaged and disengaged by a high speed clutch 24.

  In such a continuously variable transmission, in a so-called low speed mode state in which the low speed clutch 23 is connected and the high speed clutch 24 is disconnected, the power of the input shaft 3 is transmitted to the output shaft 21 via the ring gear 17. Reportedly. Then, by changing the gear ratio of the toroidal continuously variable transmission 1, the gear ratio of the continuously variable transmission, that is, the gear ratio between the input shaft 3 and the output shaft 21 changes. In such a low speed mode state, the speed ratio of the continuously variable transmission as a whole changes to infinity. In other words, by adjusting the transmission ratio of the toroidal-type continuously variable transmission 1, the rotation state of the output shaft 21 with the input shaft 3 rotated in one direction is changed between the forward rotation and the reverse rotation with the stop state interposed therebetween. Conversion is possible.

  On the other hand, in a so-called high speed mode state in which the low speed clutch 23 is disconnected and the high speed clutch 24 is connected, the power of the input shaft 3 is output through the first and second transmission shafts 10 and 13 to the output shaft 21. To be told. And the gear ratio as the whole continuously variable transmission changes by changing the gear ratio of the toroidal type continuously variable transmission 1. In this case, as the transmission ratio of the toroidal type continuously variable transmission 1 is increased, the transmission ratio of the continuously variable transmission as a whole is increased.

  The continuously variable transmission as described above includes two planetary gears 8 and 9 that are fixed to the planetary gear type transmission 2 so as to be integrally rotatable on the same axis by the first transmission shaft 10. The sun gears 15 and 11 arranged on the same axis mesh with the gears 8 and 9, respectively. In addition, two planetary gears 8 and 9 are arranged in a plurality of sets, for example, 3 sets or 4 sets around the sun gears 15 and 11 at intervals.

Also in the example shown in Patent Document 2, as shown in FIG. 15, in the planetary gear type transmission 2, planetary gears 8 and 9 are fixed to both ends of the first transmission shaft 10, respectively. The two planetary gears 8 and 9 thus formed are supported by the carrier 7.
Further, the planetary gear 8 is engaged with a sun gear 15 which is fixedly provided at a distal end portion of a hollow rotating shaft 14 whose base end portion is coupled to the output side disk 5.
The planetary gear 9 is meshed with a sun gear 11 fixed to one end of the second transmission shaft 13.

That is, the example shown in FIG. 15 also includes two planetary gears 8 and 9 that are coaxially and rotatably fixed by the first transmission shaft 10, and each of the two planetary gears 8 and 9 includes Separate sun gears 15 and 11 arranged on the same axis mesh with each other. In the example shown in FIG. 15, the planetary gear 16 is not supported by the carrier 7, and only two planetary gears 8 and 9 that are integrally formed are supported by the carrier 7.
Reference numeral 26 denotes a trunnion, and the trunnion 26 swings around a pair of pivots that are in a twisted position with respect to the rotation center axes of the disks 4 and 5 and are provided concentrically with each other. The power rollers 6 and 6 are rotatably supported.

  Similarly, there is proposed a continuously variable transmission having two planetary gears 8 and 9 that are coaxially arranged and fixed so as to be integrally rotatable, and the planetary gears 8 and 9 are helical gears. (For example, see Patent Document 3).

JP 2000-220719 A US Pat. No. 5,607,372 JP-A-9-210152

  By the way, the planetary gear type transmission of the continuously variable transmission is provided with a plurality of sets of two planetary gears that are coaxially and rotatably fixed, and each of the two planetary gears is arranged separately on the same axis. When the sun gear is engaged, there is a problem that assembly becomes difficult.

  For example, when the speed ratio between two sun gears is other than 1, for example, the number of teeth of two planetary gears is equal to each other, and the number of teeth of two sun gears is equal to each other, a plurality of sets of two planetary gears It is difficult to match the gears and the two sun gears so that they mesh with each other, and the assembly work takes time and cost.

A gear in which gears with different numbers of teeth are coaxially integrated is called a stepped gear. Here, two planetary gears that rotate together are assumed to have different numbers of teeth and rotate together. This planetary gear is referred to as a stepped planetary gear (integrated gear).
Here, when the number of teeth is different between the front planetary gear and the rear planetary gear, for example, when the front planetary gear of a plurality of stepped planetary gears is meshed with one sun gear, The phases of the plurality of planetary gears are not necessarily aligned, and there is a high possibility that the rear planetary gear cannot be meshed with other sun gears, which makes it difficult to assemble the gears.

  Basically, if the front gear, the rear gear, and the two sun gears of a plurality of stepped planetary gears are not in phase with each other, they cannot be engaged with each other. In such a case, there is a possibility that the gears will be assembled because there is a backlash in the gears (a gap that becomes a play on the rear side in the rotation direction of the meshing portion of the teeth).

  In this case, if you do not actually rotate the gears, you can not find that the gears are out of phase, the problem will be found after assembly is completed, Reassembling may increase costs. Therefore, at the time of assembly, it is necessary to assemble the planetary gears so that the phases of the planetary gears are strictly aligned, which requires more time for assembly.

  The present invention has been made in view of the above circumstances, and a continuously variable transmission and a continuously variable transmission that can improve workability when assembling a continuously variable transmission by engaging a plurality of stepped planetary gears with two sun gears. An object of the present invention is to provide a method for assembling a transmission.

In order to achieve the object, the continuously variable transmission according to claim 1 includes an input side disk and an output side disk that are supported concentrically and rotatably with the inner side surfaces thereof facing each other. A toroidal continuously variable transmission having a plurality of power rollers sandwiched between these two discs;
And at least two sun gears arranged on the same axis, a plurality of pairs of planetary gears meshed with the two sun gears, and a carrier that supports the planetary gears so as to rotate and revolve. The planetary gears of each pair of meshing gears are coaxially fixed together so as to be rotatable integrally with each other to form an integral gear, and the planetary gears meshed with the same sun gear have the same number of teeth. And a continuously variable transmission including a planetary gear type transmission in which the two planetary gears included in each integral gear and meshing with different sun gears have different numbers of teeth.
In the planetary gears included in all the integral gears supported by the carrier, the modules are equal to each other,
The integral gears are arranged at equal intervals along the circumferential direction of the carrier;
The sum of the number of teeth of one of the planetary gears of the two planetary gears included in the integral gear and the number of teeth of the one sun gear meshing with the planetary gear is the sum of the number of teeth of the other planetary gear. Equal to the sum of the number of teeth and the number of teeth of the other sun gear meshing with the planetary gear,
These values are an integral multiple of the number of integral gears supported by the carrier.

  In the first aspect of the present invention, the planetary gear type transmission of the continuously variable transmission includes two sun gears arranged coaxially, and the planetary gears meshing with the two sun gears are coaxial. The integrated gears are configured to be integrally rotatable, and in these integrated gears, the planetary gears that mesh with the same sun gear have the same number of teeth, and are included in each integrated gear. Even if the two planetary gears meshing with the sun gear have different numbers of teeth, the assembly of the continuously variable transmission can be facilitated.

That is, it is not the case where the number of teeth of the two planetary gears is equal to each other, and the number of teeth of the two sun gears is equal to each other. Can be easily.
a. In the planetary gears included in all the integral gears supported by the carrier, the modules are equal to each other.
b. The integrated gears are arranged at equal intervals along the circumferential direction of the carrier.
c, a value obtained by adding the number of teeth of the planetary gear of one of the two planetary gears included in the integral gear and the number of teeth of the sun gear meshing with the planetary gear is the other planetary gear. It is made equal to the sum of the number of teeth of the gear and the number of teeth of the other sun gear meshing with the planetary gear.
d, these values are integral multiples of the number of integral gears supported by the carrier.

If this condition is satisfied, the planetary gear type transmission can be assembled even if the gear ratio is not set to 1 as described above. Design restrictions such as the limited speed ratio obtained by the transmission are relaxed, and the degree of design freedom increases.
Further, if the above-mentioned conditions are not satisfied, for example, if the conditions other than the condition for arranging the integrated gears at equal intervals in the circumferential direction are not satisfied, the integrated gears are equally spaced in the circumferential direction on the carrier. If arranged, there is a possibility that the gears cannot be engaged with each other, and it is necessary to make the plurality of integral gears have different shapes.

  The continuously variable transmission according to a second aspect is the invention according to the first aspect, wherein the integral gears are in phase with one of the planetary gears of the two planetary gears included in the integral gear. The other planetary gears are arranged in the same shape so that the phase arrangement of the other planetary gear is the same as

  In the invention according to claim 2, the following problems can be solved. That is, even if the condition described in claim 1 is satisfied, the phase arrangement of the other planetary gear differs from the phase arrangement of the one planetary gear among the plurality of integral gears. Then, after meshing one planetary gear with one sun gear and trying to mesh the other planetary gear with the other sun gear, the phases of the other planetary gears are slightly shifted from each other. It becomes a state. As a result, even if the other sun gear is engaged, there is a possibility that the gears cannot rotate smoothly due to some deviation between the other planetary gears.

  In other words, the integrated gear includes two planetary gears. When each planetary gear is individually formed, each planetary gear to be manufactured must be aligned unless the planetary gears are aligned. In addition, the phase relationship between the two planetary gears may be different. For example, if each integrated gear is manufactured in a state in which the gear cutting start positions of two planetary gears included in the integrated gear are used as reference points and the reference points are aligned, one planetary gear is produced. The phase arrangement of the other planetary gear is the same for each of the integrated gears.

  That is, the phase arrangement of the other planetary gear is always constant with respect to the phase arrangement of the one planetary gear so that the gearing start position of one planetary gear always coincides with the gear cutting start position of the other planetary gear. Become. In a state where the gearing start position of the other planetary gear differs from the gearing start position of one planetary gear for each production, even if the phase of one planetary gear is the same in each integral gear, the other planetary gear The phases of the two integrated gears are different, and there is a possibility that even if one sun gear is assembled as described above, the other sun gear cannot be assembled.

Therefore, by forming all of the integrated gears in the same shape, a plurality of integrated gears supported by the carry can be securely meshed with the two sun gears, and each of the integrated gears is included in each of the integrated gears. If one planetary gear of the two planetary gears is in phase with one sun gear, the other planetary gear is in phase and the other sun gear is easily assembled It becomes.
Moreover, parts management becomes easy by making all the integral gears into parts of the same shape.

  The continuously variable transmission according to claim 3 is the continuously variable transmission according to claim 2, wherein the planetary gear constituting the two planetary gears included in the integral gear is provided on the outer peripheral surface of the integral gear. And a planar portion formed in a planar shape corresponding to a predetermined position on the phase of the teeth of the planetary gear portion, and the orientation of the planar portion is adjusted to be the same between the integrated gears. Thus, the phases of the plurality of integrated gears supported by the carrier can be matched.

In the continuously variable transmission according to claim 3, on the outer peripheral surface of the integral gear, there is a planetary gear portion constituting two planetary gears included in the integral gear, and the phase of the teeth of the planetary gear portion. Therefore, by aligning the positions (orientations) of these planes, the phase of the two planetary gears can be adjusted between the plurality of integral gears as described above. Can be matched to each other.
In other words, the plane portion serves as a reference mark for setting the phase of the two planetary gears of the integral gear to a predetermined arrangement. It has become. That is, by bringing a flat surface into contact with the flat portion, the phases of the integrated gears can be easily matched using a jig or the like that matches the phases of the two planetary gears of the integrated gears.

The assembly method of the continuously variable transmission according to claim 4 is an assembly method of the continuously variable transmission when the continuously variable transmission according to claim 2 or 3 is assembled,
When the sun gear is meshed with the integral gear supported by the carrier after the integral gear is attached to the carrier,
After aligning the phases of the plurality of integral gears attached to the carrier with each other, a jig for maintaining the phase relationship between the integral gears is attached to the integral gear,
Next, with the jig attached to the integrated gear, one of the two sun gears is replaced with one of the sun gears of two planetary gears included in the plurality of integrated gears. One of the planetary gears meshed with the gear is meshed and assembled.

  In the method for assembling the continuously variable transmission according to claim 4, when assembling the continuously variable transmission having an integral gear that satisfies the conditions described in claims 1 and 2 above, Attach the sun gear to one planetary gear of these integrated gears while keeping the phases of all the integrated gears attached to the carrier with the jigs that match the phases of the body gears and maintain this phase. become. In this case, one planetary gear of each pair of gears is in phase with each other, so that the sun gear can be easily attached while meshing with one planetary gear.

Further, in a state where one planetary gear is engaged with the sun gear, the planetary gears are rotated in conjunction with the sun gear engaged. In this state, the other planetary gears are in phase with each other, and even if the jig is removed, the other sun gear can be easily meshed with the other planetary gear and assembled.
Therefore, in a state where one planetary gear meshes with one sun gear, even if the jig is removed, the other planetary gear is kept in phase with each other. Gears can be engaged.

The jig needs to have a shape that does not interfere with the engagement of one sun gear and one planetary gear. In other words, the jig may have a shape that interferes with the engagement of the other sun gear and the other planetary gear. In this case, the jig may be removed when one sun gear is attached.
That is, if only one sun gear is attached using a jig, the other sun gear can be easily assembled without a jig.

  A method for assembling the continuously variable transmission according to claim 5 is the gear according to claim 4, wherein the jig has the same tooth arrangement as one of the two sun gears. The gear-type jig is formed in a state where the gear-type jig is meshed with one of the planetary gears that meshes with one of the sun gears, and the other planetary gear is It is characterized by being assembled with the sun gear.

  In the invention according to claim 5, the gear-type jig has the same tooth arrangement as one of the two sun gears, that is, can function as the same gear as one of the sun gears. Thus, when this gear mold jig is engaged with one planetary gear of an integral gear whose phase is matched on the carrier, one planetary gear is a gear type as in the state where one sun gear is engaged. Even if the planetary gear rotates when the gear-type jig is set with the gear-type jig set, the phase of each planetary gear is kept in phase. The

In this state, since the phases of the other planetary gears are also in agreement, the other planetary gear can be easily meshed with the other sun gear and assembled.
In the state where the other planetary gear is meshed with the other sun gear, the other planetary gear can rotate in conjunction with the other sun gear even if the gear-type jig is removed from the one planetary gear. Even if this planetary gear rotates, the other planetary gears are held in phase with each other. In this state, the phase of one planetary gear is in phase with each other as described above, so the gear-type jig is removed and one sun gear is easily meshed with one planetary gear and assembled. Can do.

  The method for assembling the continuously variable transmission according to claim 6 is the invention according to claim 4, wherein the jig is detachably engaged with each of the carrier and the integrated gear attached to the carrier. One of the two planetary gears included in the integrated gear that is a rotation restricting jig for restricting the rotation of the integral gear with respect to the carrier and whose rotation is restricted by the rotation restricting jig. One of the sun gears meshed with the planetary gear is meshed with the planetary gear and assembled.

In the invention described in claim 6, after the phase is arranged in all of the integral gears attached to the carrier, the rotation of the integral gear is regulated by the rotation regulating jig, and the phases of the integral gears are in phase. Therefore, one sun gear and the other sun gear can be easily attached to the integral gear.
As the rotation restricting jig, for example, any one may be used as long as it enters between the carrier and the integral gear and stops the rotation of the integral gear with respect to the carrier. The integral gear of the carrier and the integral gear is pushed into the interval along the rotation direction of the integral gear, and elastically deforms and by the elasticity, the integral gear is pressed against the carrier along the axial direction. The rotation of the integrated gear may be restricted by pressing against the carrier.

  According to the continuously variable transmission and the assembly method of the continuously variable transmission of the present invention, two planetary gears meshing with different sun gears are integrated into a continuously variable transmission that combines a toroidal transmission and a planetary gear type transmission. Even when there is a stepped planetary gear that can be rotated, the workability when assembling the continuously variable transmission by engaging two sun gears with the stepped planetary gear can be improved.

It is a perspective view which shows the integral gear of the continuously variable transmission of 1st Embodiment of this invention. It is a perspective view which shows arrangement | positioning of the said integral gear. It is a perspective view which shows the said integrated gear in which the plane part was formed. It is a perspective view which shows the carrier with which the said integral gear was attached. It is a figure for demonstrating the phase alignment method of the integral gearwheel attached to the said carrier. It is a perspective view for demonstrating attachment of the gear type jig | tool to the said integral gear. It is a perspective view for demonstrating attachment of the gear type jig | tool to the integral gear attached to the said carrier. It is a perspective view for demonstrating attachment of the integral gear attached to the carrier to the sun gear attached to the toroidal type continuously variable transmission of a continuously variable transmission, and to which the gear type jig | tool was attached. It is a perspective view for demonstrating attachment of the rotation control jig | tool as a modification of the said jig | tool. It is a perspective view which shows the integrated gear attached to the carrier of the continuously variable transmission of 2nd Embodiment of this invention. It is a perspective view which shows the integrated gear of 2nd Embodiment. It is a side view which shows the integrated gear attached to the carrier of 2nd Embodiment. It is sectional drawing for demonstrating the phase alignment of each integrated gear of 2nd Embodiment. It is a schematic sectional drawing which shows the conventional continuously variable transmission. FIG. 15 is a schematic cross-sectional view showing a conventional continuously variable transmission having a configuration different from that of the continuously variable transmission shown in FIG. 14.

  Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. The continuously variable transmission of the first embodiment is characterized by an integral gear (a stepped planetary gear) in which a pair of planetary gears provided in the planetary gear type continuously variable transmission of the continuously variable transmission is fixed integrally. In the following, only the characteristic part of this embodiment will be referred to, and the other parts will be described with reference to FIG. 14 and the same reference numerals as those in FIG.

  FIG. 1 is a perspective view showing an integrated gear of a continuously variable transmission according to a first embodiment of the present invention, and FIG. 2 is a perspective view showing an arrangement of the integrated gear. 3 is a perspective view showing the integrated gear having a flat surface portion, FIG. 4 is a perspective view showing a carrier to which the integrated gear is attached, and FIG. 5 is a phase alignment of the integrated gear attached to the carrier. FIG. 6 is a perspective view for explaining the attachment of the gear-type jig to the integral gear, and FIG. 7 is a perspective view of the gear-type jig to the integral gear attached to the carrier. FIG. 8 is a perspective view for explaining the mounting, and FIG. 8 is a view showing the mounting of the integrated gear attached to the carrier to the sun gear attached to the toroidal type continuously variable transmission of the continuously variable transmission and attached to the gear type jig. It is a perspective view for demonstrating.

An integrated gear (stepped planetary gear) 31 shown in FIG. 1 is formed by integrally joining the planetary gear 8 and the planetary gear 9 of the continuously variable transmission shown in FIG. 14 and these two planetary gears 8 and 9 on the same axis. The first planetary gears 8 and 9 are coaxially configured to be integrally rotatable.
Then, as shown in FIG. 14, the front planetary gear 8 meshes with the front sun gear 15, and the rear planetary gear 9 meshes with the rear sun gear 11.
The integral gear 31 is formed in a cylindrical shape whose central portion along the axial direction is a cylindrical cavity that penetrates the integral gear 31 in the axial direction, and is supported by the carrier 7 inside. It arrange | positions in the state which the rotating shaft penetrated, and it can rotate around the said rotating shaft.

  The integrated gear 31 is supported by the carrier 7 so as to rotate and revolve. The integrated gear 31 supported by the carrier 7 includes three integrated gears 31 along the circumferential direction as shown in FIG. They are lined up. In addition, the sun gears 15 and 11 are arrange | positioned in the center part of these integral gears. The three integrated gears 31 are arranged at the same interval along the circumferential direction. For example, when viewed from the center of these three integrated gears 31 (the rotation center of the sun gears 15 and 11). , The rotation center of the integral gear 31 is arranged every 120 degrees. That is, the integrated gear 31 is arranged at equal intervals along the circumferential direction.

In this example, the toroidal type continuously variable transmission 1 is arranged on the front side of the integral gear 31, and the front planetary gear 8 is connected to the toroidal type continuously variable transmission 1 from the rear planetary gear 9. On the side closer to
Each of the integral gears 31 has a rotation center axis that is parallel to each other, and the rotation center axis is the rotation center axis of each disk 4, 5 of the toroidal-type continuously variable transmission 1 (the axis of the input shaft 3. Direction).

In these three integrated gears 31, the front planetary gears 8 all have the same number of teeth. The rear planetary gears 9 all have the same number of teeth. The front planetary gear 8 and the rear planetary gear 9 have different numbers of teeth.
Further, the tooth shapes and sizes of the three integrated gears 31 are the same, and the tooth shapes and sizes of the two planetary gears 8 and 9 in the integrated gear 31 are the same.

Therefore, in each integrated gear 31, the two planetary gears have the same module, and the integrated gear 31 also has the same module. In this example, the two planetary gears 31 are included in the three integrated gears 31. All six planetary gears 8 and 9 have the same module.
The module is a value obtained by dividing the pitch circle diameter of the gear by the number of teeth of the gear, and indicates the size of the gear teeth.

A value (a + b) obtained by adding together the number of teeth a of one planetary gear 8 of the two planetary gears 8 and 9 of the integral gear 31 and the number of teeth b of the sun gear 15 meshing with the planetary gear 8, The sum (c + d) of the number of teeth c of the other planetary gear 9 and the number of teeth d of the sun gear 11 meshing with the planetary gear 9 is equal (a + b = c + d).
The sum (a + b = c + d) of the number of teeth (a, c) of the planetary gears 8 and 9 and the number of teeth (b, d) of the sun gears 15 and 11 meshing with the planetary gears 8 and 9 7 is an integral multiple of the number (n) of integral gears 31 supported by 7, that is, the number (n) of integral gears 31 meshing with sun gears 15 and 11 (a + b = c + d = n · k: k is an integer) It has become. Here, since three integrated gears 31 are arranged on the carrier 7, a + b = c + d is a multiple of three.

In addition, each integrated gear 31 has the same shape so that the arrangement (phase) of the teeth of the planetary gear 9 is equal to the arrangement (phase) of the teeth of the planetary gear 8. For example, by arranging the gear cutting start position of the planetary gear 8 and the gear cutting start position of the planetary gear so as to overlap in the axial direction, the phase of the teeth of the planetary gear 8 is matched with each integral gear 31. Can do.
Note that if the relationship between the phase of the planetary gear 8 and the phase of the planetary gear 9 is the same in all the integral gears 31, the reference need not be the gear cutting start position. Further, it is not necessary that the phase reference of the planetary gear 8 and the phase reference of the planetary gear 9 overlap in the axial direction, and a line segment that connects the phase reference of the planetary gear 8 and the rotation center of the integral gear 31. And the angle formed by the line segment connecting the phase reference of the planetary gear 9 and the rotation center of the integral gear 31 may be the same for all the integral gears 31.

A flat portion 32 along the axial direction is formed on the outer peripheral surface of the first transmission shaft 10 of the integral gear 31. In this example, three plane portions 32 are provided, and when the adjacent plane portions 32 are extended and intersected, the angle between the adjacent plane portions 32 is 60 degrees. That is, they are arranged so as to form an equilateral triangle when these three planes are extended and intersected when viewed from the axial direction.
Further, since the integrated gear 31 has the same shape as described above, the reference of the phase of the teeth of the planetary gears 8 and 9 and the arrangement of the plane portions 32 are the same for all the integrated gears 31. It is supposed to be the same. Note that, on the outer peripheral surface of the integral gear 31, the planetary gear portion 8a on the front side where the teeth of the planetary gear 8 are formed, the planetary gear portion 9a on the rear side where the teeth of the planetary gear 9 are formed, And the flat portion 32 formed on the outer peripheral surface of the first transmission shaft 10.

  The integrated gear 31 is rotatably held by the carrier 7, and the carrier 7 is connected to the input side disk 4 on the rear side of the toroidal type continuously variable transmission 1 so as to be integrally rotatable, for example. A substantially annular plate-shaped front support plate 71, and on the rear side of the front support plate 71, arranged in parallel and coaxially with the front support plate 71, and an annular plate-shaped rear support plate 72; Between the front support plate 71 and the rear support plate 72, an intermediate support plate 73 having an annular plate shape is disposed in parallel and coaxially with the front support plate 71 and the rear support plate 72. .

  Further, a connection wall portion 74 that connects the front support plate 71 and the intermediate support plate 73 and a connection wall portion 75 that connects the intermediate support plate 73 and the rear support plate 72 are provided. The connecting wall 75 is provided in a continuous state along the axial direction. The connection wall portions 74 and 75 are divided into three parts between the front support plate 71 and the rear support plate 73 and excluding the central portion where the front support plate 71 and the rear support plate 73 have openings. Three each are provided. Further, the connection wall portions 74 and 75 are arranged along the radial direction of the three support plates 71, 72, and 73.

  One integrated gear 31 is disposed in each of the three spaces partitioned by the connection wall portions 74 and 75, meshes with the planetary gear 8 on the front side of the integrated gear 31, and is connected to the ring gear 17. An intermeshing planetary gear 16 is arranged. The planetary gear 16 is disposed between the front support plate 71 and the intermediate support plate 73 so as to mesh with the planetary gear 8 on the front side.

  The front support plate 71 and the rear support plate 72 are provided with a rotating shaft so as to pass through the cylindrical integrated gear 31 with the integrated gear 31 disposed therebetween. The front and rear end portions are respectively supported by the front support plate 71 and the rear support plate 72, whereby each integrated gear 31 is attached to the carrier 7 so as to be rotatable around the axis. The planetary gear 16 that meshes with the planetary gear 8 and the ring gear 17 is formed in a substantially cylindrical shape, and is disposed between the front support plate 71 and the intermediate support plate 73. The rotating shaft for the planetary gear 16 is disposed so as to penetrate the cylindrical planetary gear 16, and the front and rear end portions are supported by the front support plate 71 and the intermediate support plate 73. Thereby, the planetary gear 16 is supported by the carrier 7 in a state of being rotatable around the rotation axis.

  In addition, a circular hole is formed in the center of the annular plate-like intermediate support plate 73 as in the case of the front support plate 71 and the rear support plate 72, and one portion is provided in a portion where each integrated gear 31 is disposed. A notch 77 that can pass through the first transmission shaft 10 of the body gear 31 is provided. Further, the notch 77 is provided from the outer peripheral edge of the intermediate support plate 73 to a part on the outer peripheral side from the circular hole, and the outer peripheral part is open.

The phases of all the integral gears 31 supported by the carrier 7 can be adjusted by the three flat portions formed in each integral gear 31.
In this example, for example, one of the three plane portions includes a reference position of the planetary gear 8 and the planetary gear 9 (angle: for example, a black dot shown in FIG. 5 or the like). The phase of the integrated gear 31 can be adjusted by arranging the plane portion 32 horizontally on the upper side. That is, the plane part 32 has the plane part 32 formed in a planar shape corresponding to a predetermined position on the phase of the teeth of the planetary gears 8 and 9 (planetary gear parts 8a and 9a). By setting the angle of the plane portion 32 to a predetermined angle for all the integral gears 31, the phases of all the integral gears 31 can be made the same.

In addition, when the plane including the position serving as the reference for the phase is set to be horizontal on the upper side, one of the remaining plane sections 32 of the three plane sections 32 faces the lower right side and the other is the lower left section. Arranged to face diagonally.
And since each plane part 32 is formed so that it may cross at 60 degrees as mentioned above, when plane part 32 including the position used as a reference is arranged horizontally facing up, with respect to it The plane part 32 facing the lower right is arranged along the left diagonal by 60 degrees, and the plane part facing the lower left is arranged along the diagonal right by 60 degrees.

FIG. 5 shows an outline of a phase matching jig for matching the phases of these integrated gears 31 supported by the carrier 7.
In the alignment jig, three contact members 41, that is, the same number of contact members 41 as the integrated gear 31 disposed on the carrier 7, are disposed at equal intervals along the circumferential direction. For example, here, the contact member 41 is arranged at the center of each side of the equilateral triangle. Moreover, it arrange | positions in the center of each edge | side of the regular polygon which has the edge | side (corner) used as the number of the integral gearwheels 31 arrange | positioned at the carrier 7. FIG. And the side surface which faces the inner side of these contact members 41 is in the state along the tangent direction of the inscribed circle of a regular polygon.

Here, the inner side surfaces of the three abutting members 41 are arranged at each side portion of the equilateral triangle, arranged along the tangential direction of the inscribed circle of the equilateral triangle, The side faces 60 degrees apart.
In this example, the regular triangle is an inverted regular triangle, and one abutting member 41 is arranged on the upper side so that the inner side surface is horizontal, and the inner side surface is obliquely left on the lower left side (the upper side is on the left side). An abutting member 41 facing (inclined) is disposed, and an abutting member 41 whose inner side surface faces obliquely right (upper side tilts to the right) is disposed in the lower right.

Further, as shown in FIG. 5, these contact members 41 are in a state of closing the open portion of the notch portion 77 where the above-described outer peripheral edge side of the intermediate support plate 73 is opened with the carrier 7 disposed therein. In addition to being disposed, the first transmission shaft 10 of the integral gear 31 is brought into contact with the first transmission shaft 10, and at this time, the flat gear portion 32 of the first transmission shaft 10 is contacted.
In addition, in the open part on the outer peripheral edge side of the notch 77 of the intermediate support plate 73, the first transmission of the integrated gear 31 supported by the carrier 7 and the line connecting the ends of the left and right outer peripheral edges. When the integrated gear 31 is rotated so that the position of the outer peripheral surface of the shaft 10 is substantially coincident with the position of the plane portion 32 formed on the first transmission shaft 10, the line and the plane portion are aligned. 32 substantially matches.

Each contact member 41 is supported by a support member (not shown), but the support member is disposed outside the contact member 41. Further, the support member is rotatable so that the inner surface of the contact member 41 can be rotated more than 90 degrees from the horizontal state with the support member 41 supporting the contact member 41 on the upper side, for example. The upper part of the contact member 41 may be openable.
In addition, when closed, the inner side surface of the contact member 41 needs to be positioned horizontally.

  By using such a phase matching jig, the plane portion 32 formed on the first transmission shaft 10 of the integral gear 31 is brought into surface contact with the inner side surface of the abutting member 41 so as to be supported by the carrier 7. In addition, the phases of all the integrated gears 31 can be matched. In addition, since each plane part 32 of the integral gear 31 has a predetermined arrangement position, for example, it is necessary to arrange the plane part 32 including the reference position so as to face upward as described above.

Even if all the integrated gears 31 of the carrier 7 are in a state in which the flat surface portion 32 is in contact with the inner side surface of the contact member 41, if the arrangement of the flat surface portions 32 is different, the planetary gears are different. Since the phases do not become the same due to the number of teeth of 8 and 9, etc., one of the three plane portions 32 is set as a reference plane portion 32, and the reference plane portion 32 has the same orientation in each integrated gear 31. It is necessary to face it.
In the integrated gear 31, for example, it is preferable to mark the reference position of the phase of each planetary gear 8, 9 and the reference plane portion 32, and these marks are the same in each integrated gear 31. By making it face the direction, the phases of the integrated gears 31 can be matched. The plane portion 32 functions as a mark for the two planetary gears 8 and 9 of the integrated gear 31. In this example, since there are three plane portions 32, a plane serving as a reference of these plane portions 32 is provided. The part 32 may be provided with a mark as described above. Moreover, each plane part 32 is good also as a different shape, for example, the distance from the axial center of the integral gear 31 of the plane part 32 may differ, and in this case, the contact member which contacts each plane part 32 The position of the inner side surface of 41 is also different for each contact member 41, and when the corresponding flat surface portion 32 and the contact member 41 face each other, the flat surface portion and the contact member 41 are contacted at a fixed position. If the non-corresponding flat portion 32 and the abutting member 41 face each other, the flat portion 32 and the abutting member 41 cannot be in contact with each other, or conversely, the flat portion 32 is on the near side of the fixed position. Therefore, a structure may be adopted in which the position of the carrier 7 is displaced due to contact with the contact member 41.

6-7 is for demonstrating the assembly method of the continuously variable transmission provided with the above-mentioned integral gear 31, and the assembly method is carried out to the carrier 7, such as the integral gear 31, etc. After the gears to be supported are attached, the phases of the integrated gears 31 are adjusted as described above, and then the phases of the integrated gears 31 are not shifted by the gear-type jig. The sun gears 15 and 11 are meshed with the planetary gears 8 and 9 and incorporated.
Here, the gear-shaped jig 51 is supported by the carrier 7 and meshes with each of the integrated gears 31 in a phase-matched state, and holds the phase of the integral gears in a matched state. .

The gear shape of the gear type jig 51 has the same gear shape as the sun gear 11 meshing with one (rear side) planetary gear 9 of the two planetary gears 8 and 9 included in the integral gear 31. It has become. The gear-type jig 51 may have a different shape from the sun gear 11 as long as the tooth portion meshing with the planetary gear 9 has the same shape as the sun gear 11, and the axial direction of the gear portion. The thickness along the line may be different.
The gear-type jig 51 meshes with one planetary gear 9 that meshes with the sun gear 11 to be assembled later in the assembly order of the two planetary gears 8 and 9 of the integral gear 31. The value indicating the shape of the gear such as the number of teeth of the sun gear 11 meshing with 9, the pitch circle diameter, and the module is the same as that of the sun gear 11.

The gear-type jig 51 is provided with a shaft portion 52 for holding the gear-type jig 51 by an operator or a machine. The shaft portion 52 is a columnar or cylindrical member extending along the axis of the gear portion of the gear-type jig 51.
In the method of assembling the continuously variable transmission using such a gear-type jig 51, after the integrated gear 31 and the planetary gear 16 are attached to the carrier 7 as described above, the above-described phase matching jig is used to In this manner, the phases of the integrated gear 31 supported by the carrier 7 are matched. Before removing the carrier 7 from the phase matching jig, as shown in FIG. 7, the gear-type jig 51 is connected to the integrated gear 31 in a state where the rotation is restricted in a phase-matched state by the phase matching jig. Is in a state of meshing. In FIG. 7, the phase matching jig is not shown. In FIG. 6, the phase matching jig and the carrier 7 are not shown, and the integrated gear 31 is easily seen.

At this time, the gear-type jig 51 is inserted into the central part of the plurality of integrated gears 31 arranged along the circumferential direction from the circular hole of the rear support plate 72 of the annular plate shape of the carrier 7, The planetary gear 9 of the integral gear 31 and the gear jig 51 are rotated while the shaft 52 is slightly rotated around the axis so that the teeth of the gear jig 51 are aligned with the teeth of the integral gear 31. And bite.
In this example, all of the gears described above are helical gears, and it is necessary to rotate at least one gear when meshing with each other.

Next, with the gear-type jig 51 meshing with all the planetary gears 9 and being supported by the planetary gears 9, the carrier 7 is taken out of the phase matching jig provided with the contact member 41, as shown in FIG. Next, the position of the carrier 7 is aligned with the sun gear 15 portion fixed to the hollow rotary shaft 14 of the toroidal type continuously variable transmission 1 in advance.
Then, the planetary gear 8 of the integral gear 31 supported by the carrier 7 is meshed with the sun gear 15. At this time, the carrier 7 is moved forward so that the sun gear 15 is inserted from the circular hole of the annular front plate-like support plate 71 of the carrier 7.
At this time, in order to align the position of the teeth of the sun gear 15 and the position of the teeth of the planetary gear 8, at least one of these gears needs to rotate, and since these gears are helical gears, In a state where the positions are aligned, at least one of the gears is rotated and meshed.

At this time, when the gear-type jig 51 is used, each planetary gear 8 can be rotated in conjunction with the gear-type jig 51 and the phase of each planetary gear 8 is rotated even if it rotates. Since there is no deviation, the sun gear 15 and the planetary gear 8 can be engaged with each other while rotating both the sun gear 15 and the planetary gear 8.
In the state in which the planetary gear 8 is engaged with the sun gear 15, all the other planetary gears 9 of the integral gear 31 are in phase with each other because of the above-described phase alignment. 9 can be easily meshed with the sun gear 11.
Further, in order to mesh the sun gear 11 with the planetary gear 9, it is necessary to remove the gear-type jig 51. At this time, the sun gear 15 is already meshed with the planetary gear 8. Thus, since all the integrated gears 31 are held in phase, there is no problem even if the gear jig is removed.

As a result, the operation of meshing the two sun gears 15 and 11 with the planetary gears 8 and 9 having different tooth numbers of the planetary gear type transmission and the stepped planetary gears integrated is completed. become.
In the continuously variable transmission as described above, it is possible to reliably assemble a planetary gear type transmission even if an integral gear 31 (stepped planetary gear) in which two planetary gears are integrated is used. That is, since the planetary gear type transmission has the stepped planetary gear, it can be prevented that the assembling becomes difficult or the assembling becomes impossible.
Further, since the assembly is performed with the phases of all the integral gears 31 attached to the carrier 7 being matched, the phase of one of the planetary gears 8 and 9 of the integral gear 31 is shifted and cannot be assembled on the way. It is possible to prevent the situation from occurring and the need to disassemble and reassemble. That is, it is possible to prevent a decrease in work efficiency due to re-working due to failure in assembly. In addition, the assembled planetary gears 8 and 9 and the sun gears 15 and 11 have a phase shift of, for example, one tooth in an assembled state due to a slight phase shift. Thus, it is possible to prevent the power transmission efficiency from being low, resulting in a defective product, and a decrease in yield.

  In the above example, the gear-type jig 51 is used to keep the phases of the integrated gears 31 in phase with each other and mesh with one of the sun gears 15. The jig to be held in the state is not limited to the gear-type jig 51. For example, if the above-described phase matching jig is attached to the carrier 7 and is small, the phase matching jig can be used. May be used to mesh with the sun gear 15 in a state where the phases of the integrated gear 31 are matched.

  Also, as a jig, for example, an elastically deformable rotation restricting jig 53 is inserted between the end face of the integrated gear 31 and the front support plate 71 or the rear support plate 72 in a compressed and deformed state. By pressing the rotation restricting jig 53 against the integrated gear 31 with elasticity, the phase of each integrated gear 31 is changed to a state in which the integrated gear 31 in a phase is incapable of rotation by the frictional force based on the pressing force. It is good also as what hold | maintains in the state which matched.

The rotation restricting jig 53 is, for example, a bent rectangular metal plate that functions as a leaf spring. For example, the rotation restricting jig 53 may be a synthetic resin plate and is elastic in a compressed state. Any shape that can be deformed and can be inserted between the end face of the integrated gear 31 and the front support plate 71 or the rear support plate 72 may be used.
The rotation restricting jig 53 is inserted at a position between the end face of the integrated gear 31 and the washer or between the washer and the carrier 7 when there is a washer between the end face of the integrated gear 31 and the carrier 7. It may be between.
Further, the rotation restricting jig 53 only needs to have a structure in which the integral gear 31 cannot rotate with respect to the carrier 7. For example, the rotation restricting jig 53 can be engaged with both the teeth of the integral gear 31 and the carrier 7. It may be such that rotation of the integral gear 31 is prevented.

In the case of the rotation restricting jig 53, the rotation of the integral gear 31 is prevented, so that the planetary gear 8 and the sun gear 15 are rotated while the integral gear 31 is rotated as in the gear mold jig 51 described above. However, if the sun gear 15 side is rotatable, it can be meshed without any problem.
Further, the rotation restricting jig 53 can be manufactured at a lower cost than the gear-type jig 51.

After the sun gear 15 is engaged with the planetary gear 8, the rotation restricting jig 53 is removed and the sun gear 11 is engaged with the planetary gear 9.
In this case, if the sun gear 15 can be rotated by removing the rotation restricting jig 53, the integrated gear 31 can also be rotated, and the integrated gear 31 and the sun gear 11 can rotate. In this state, the planetary gear 9 and the sun gear 11 can be engaged with each other.

  10 to 13 show a second embodiment of the present invention, and FIG. 10 is a perspective view showing an integrated gear attached to a carrier of a continuously variable transmission according to the second embodiment of the present invention. 11 is a perspective view showing the integrated gear of the second embodiment, FIG. 12 is a side view showing the integrated gear attached to the carrier of the second embodiment, and FIG. 13 is each integrated type of the second embodiment. It is sectional drawing for demonstrating the phase alignment of a gearwheel. Note that the carrier 7 and the integral gear 31 in FIG. 13 show a cross section along the one-dot chain line a in FIG.

In the first embodiment, the carrier 7, the integrated gear 31, and the sun gears 15 and 11 correspond to the gears of the conventional continuously variable transmission shown in FIG. 14, whereas the second embodiment In FIG. 1, each gear corresponds to the continuously variable transmission shown in FIG.
In the continuously variable transmission shown in FIG. 15, only the integrated gear 31 is supported on the carrier 7 that supports the integrated gear 31, and the planetary gear 16 is not supported, but the planetary gear 16 is supported. Therefore, the intermediate support plate 73 is not provided. As will be described later, four integral gears 31 are arranged on the carrier 7, and the planar portion 32 of the integral gear 31 is one.

  The conditions that the integrated gear 31 should satisfy are the same as those in the first embodiment, and the integrated gear 31 supported by the carrier 7 has the same shape, and the planet in front of the integrated gear 31. The number of teeth is different between the gear 8 and the rear planetary gear 9, and the sum of the number of teeth of the planetary gear 8 and the number of teeth of the sun gear 15 is the sum of the number of teeth of the planetary gear 8 and the number of teeth of the sun gear 11. Is equal to. The number that is the sum is an integral multiple of the number of integral gears 31 supported by the carrier 7. Here, since the four integral gears 31 are supported by the carrier 7, the number to be the sum is a multiple of four.

The carrier 7 includes a front support plate 71, a rear support plate 72, and a connection wall portion 76 that connects them.
Similarly to the above example, the integrated gear 31 is arranged in a state of being bridged between the front support plate 71 and the rear support plate 72 and penetrates through the integrated gear 31 arranged therebetween. Is rotatably supported by a rotating shaft.

  In this example, there are four integrated gears 31 that are supported by the carrier 7 and arranged in a circumferentially arranged state at equal intervals. The connection wall portion 76 is arranged in a substantially cross shape so as to divide the space in which each integrated gear 31 is arranged, and the circular shape of the front support plate 71 and the rear support plate 72 each having an annular plate shape at the center. A cylindrical portion corresponding to the hole is formed. The upper part of the cylinder is formed in a circular shape on the inner peripheral side.

In the second embodiment, one integral gear 31 is added to the first embodiment, but three planetary gears 16 that are meshed with each planetary gear 8 of the integral gear 31 in the first embodiment are combined. The space around each integrated gear 31 is widened.
Accordingly, since it is also possible to easily insert a plate-like member into the carrier 7, in the first embodiment, the phase matching having the contact member arranged on the outer peripheral portion of the carrier 7 is performed. Instead of the jig, a phase matching jig 36 having an abutting portion 34 abutting against the flat portion 32 of the integrated gear 31 is used inside the carrier 7.

There are two phase matching jigs 36. The phase matching jig 36 for phase matching of the upper left and right two of the four integrated gears 31 and the phase matching of the upper and lower two integral gears 31 on the right side are performed. The phase matching jig 36 is used.
These phase matching jigs 36 have a U-shaped cross section in which two parallel plate bodies are joined by plate bodies orthogonal to them.

The upper plate body is a contact portion 34 that contacts the flat surface portion 32 of the upper integrated gear 31, and the lower plate body is a contact portion 35 that contacts the lower integrated gear 31. The lower surfaces of the contact portions 34 and 35 are contact surfaces that contact the flat portion 32.
Further, the distance between the contact portions 34 and 35 corresponds to the distance between the integrated gears 31 supported by the carrier 7.

  When attaching the phase matching jig 36 to the carrier 7, first, the carrier 7 is arranged between the left and right bases 37 of the installation base 38 having the bases 37, 37 on the left and right. In the installation table 38, the heights of the left and right tables 37 are the same, and the upper surfaces of these tables 37 are horizontal planes. The contact portions 34 and 35 of the phase matching jigs 36 and 36 are parallel to each other. Further, the height positions of the upper and lower contact portions 34 and 35 are the same in the left and right phase matching jigs 36 and 36.

And as above-mentioned, each contact part 34 and 35 of each phase alignment jig | tool 36 and 36 contact | abuts to the plane part 32 of another integral gear 31, respectively, and each plane part will be in the state which faced the same direction. As a result, the phases of the integrated gears 31 can be matched.
In the second embodiment, since the phase matching jigs 36 are all in contact with the flat portion 32 facing upward, it is not necessary to provide the three gear portions 32 on the integrated gear 31 as in the first embodiment. As shown in FIGS. 11 and 13, it is only necessary to provide the integrated gear 31 with only one flat portion 32 serving as a phase reference for the planetary gears 8 and 9.

After the phases of all the integrated gears 31 are matched as described above, the phase of each of the integrated gears 31 is maintained using the same gear-type jig 51 or the rotation restricting jig 53 as in the first embodiment. In this state, the sun gear 15 is engaged with one planetary gear 8 and incorporated. Next, as in the first embodiment, the gear-type jig 51 or the rotation regulating jig 53 is removed, and the sun gear 11 is engaged with the other planetary gear 9 and incorporated.
In the second embodiment, the same operational effects as those of the first embodiment can be obtained, and only one plane portion 32 needs to be provided in the integrated gear 31, so that the processing cost of the integrated gear 31 can be reduced. Can be reduced.

  The present invention relates to a continuously variable transmission using a planetary gear type transmission and a half toroidal continuously variable transmission, as well as a planetary gear type transmission and a full toroidal continuously variable transmission without a trunnion. It can also be applied to.

DESCRIPTION OF SYMBOLS 1 Toroidal type transmission 2 Planetary gear type transmission 3 Input shaft 4 Input side disk 5 Output side disk 6 Power roller 7 Carrier 8 Planetary gear 9 Planetary gear 11 Sun gear 15 Sun gear 31 Integrated gear (stepped planetary gear)
32 Plane part 51 Gear type jig (jig)
53 Rotation restriction jig (jig)

Claims (6)

A toroidal type non-rotation having an input side disk and an output side disk that are supported concentrically and rotatably with their inner surfaces facing each other, and a plurality of power rollers sandwiched between these disks. A step transmission,
And at least two sun gears arranged on the same axis, a plurality of pairs of planetary gears meshed with the two sun gears, and a carrier that supports the planetary gears so as to rotate and revolve. The planetary gears of each pair of meshing gears are coaxially fixed together so as to be rotatable integrally with each other to form an integral gear, and the planetary gears meshed with the same sun gear have the same number of teeth. And a continuously variable transmission including a planetary gear type transmission in which the two planetary gears included in each integral gear and meshing with different sun gears have different numbers of teeth.
In the planetary gears included in all the integral gears supported by the carrier, the modules are equal to each other,
The integral gears are arranged at equal intervals along the circumferential direction of the carrier;
The sum of the number of teeth of one of the planetary gears of the two planetary gears included in the integral gear and the number of teeth of the one sun gear meshing with the planetary gear is the sum of the number of teeth of the other planetary gear. Equal to the sum of the number of teeth and the number of teeth of the other sun gear meshing with the planetary gear,
These continuously variable transmissions are characterized in that these values are integral multiples of the number of the integral gears supported by the carrier.   The integrated gears are identical to each other so that the phase arrangement of the other planetary gear is the same as the phase arrangement of the planetary gear of one of the two planetary gears included in the integrated gear. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is formed in a shape.   The outer peripheral surface of the integral gear is formed in a planar shape corresponding to a predetermined position on the phase of teeth of the planetary gear portion and two planetary gears included in the integral gear. By aligning the plane portions so that the directions of the plane portions are the same between the integrated gears, the phases of the plurality of integrated gears supported by the carrier can be matched. The continuously variable transmission according to claim 2, wherein the continuously variable transmission is provided. A method for assembling the continuously variable transmission when assembling the continuously variable transmission according to claim 2 or 3,
When the sun gear is meshed with the integral gear supported by the carrier after the integral gear is attached to the carrier,
After aligning the phases of the plurality of integral gears attached to the carrier with each other, a jig for maintaining the phase relationship between the integral gears is attached to the integral gear,
Next, with the jig attached to the integrated gear, one of the two sun gears is replaced with one of the sun gears of two planetary gears included in the plurality of integrated gears. An assembly method of a continuously variable transmission, wherein the planetary gear meshing with one of the gears is meshed and assembled.   The jig is a gear-shaped jig formed in a gear shape having the same tooth arrangement as one of the two sun gears, and the gear-shaped jig is 5. The continuously variable transmission according to claim 4, wherein the other planetary gear is engaged with the other sun gear and assembled while being engaged with the one planetary gear engaged with the one sun gear. Assembly method.   The jig is a rotation restricting jig that removably engages the carrier and the integral gear attached to the carrier to restrict the rotation of the integral gear relative to the carrier, and the rotation restriction One sun gear that meshes with the planetary gear is engaged with and assembled with one of the planetary gears of the two planetary gears included in the integrated gear whose rotation is restricted by a jig. A method for assembling the continuously variable transmission according to claim 4.

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