JP4978557B2 - Friction wheel type continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission used for a power transmission device of a vehicle, and in particular, a pair of friction wheel type continuously variable transmissions are arranged to face each other and apply a pressing force between members that perform friction transmission. The present invention relates to a transmission equipped with a loading device.

  A continuously variable transmission (CVT) is a transmission capable of continuously changing the rotation speed ratio (transmission ratio) of an input / output shaft, and is widely used in the fields of vehicles, various working machines, and the like. In a vehicle, when a continuously variable transmission is used as a transmission of a power transmission device that transmits engine power to wheels, unlike a stepped transmission, continuous shifting according to the vehicle running state is possible. Thus, it is possible to realize traveling without a shift shock, and it is advantageous in terms of fuel economy of the vehicle. For the purpose of energy saving, it is also desirable to use a continuously variable transmission to convert to an appropriate rotational speed when recovering the energy at the time of vehicle deceleration or exhaust heat energy in the form of rotational power.

  The continuously variable transmission includes a mechanical type and a hydraulic type. Among mechanical type continuously variable transmissions, a V-belt is used to adjust the width of the opposing conical surface of the transmission pulley to change the speed. A V-belt type continuously variable transmission that performs the above has been put to practical use as a transmission for a vehicle power transmission device. Among mechanical continuously variable transmissions, there is a friction wheel continuously variable transmission that uses a friction wheel to transmit power by frictional force. This is because a special V belt is passed around a pulley between separated shafts. Compared with a belt-type continuously variable transmission, it has advantages such as hermetic lubrication and good unity.

  Various types of friction wheel type continuously variable transmissions are also known, and a power roller is disposed between opposing curved surfaces of a disk fixed to an input / output shaft, and the inclination of the power roller is changed to change speed. Or a planetary wheel type continuously variable transmission using a conical friction wheel (planetary wheel) arranged in a planetary manner. Among continuously variable transmissions that perform transmission using planetary wheels, there are continuously variable transmissions that can stop the rotation of the output shaft relative to the rotation of the input shaft and further reverse the rotation. For example, in Japanese Patent Laid-Open No. 3-9171, two such continuously variable transmissions are arranged opposite to each other, and the vehicle power transmission in which left and right wheels of the vehicle are independently driven by each continuously variable transmission. The device is shown. Japanese Utility Model Publication No. 39-33734 discloses a transmission in which a pair of continuously variable transmissions having the same structure are arranged symmetrically facing each other and an output is taken out from a single output shaft.

  By the way, in a friction wheel type continuously variable transmission, in order to ensure the frictional force between the members which perform friction transmission, and to perform reliable power transmission, it is necessary to provide pressing force between the members which contact. A device that applies a pressing force is called a loading device (pressure-regulating joint). Generally, a ride-on disk placed on an output shaft or the like is used to adjust the pressing force according to a load to be transmitted. The cam is configured to generate a thrust force corresponding to the transmission torque and to direct the thrust force to the pressing force. A continuously variable transmission including such a loading device and using a conical friction wheel arranged in a planetary manner is disclosed in Japanese Patent Application Laid-Open No. 5-187509 as an example.

  FIG. 6 shows a continuously variable transmission described in Japanese Patent Application Laid-Open No. 5-187509. In FIG. 6A, engine power is input to a bevel gear 102 that is rotatably fitted around the output shaft 101, and rotates a carrier 103 that is integrated with the bevel gear 102. A conical friction wheel 105 is rotatably supported on a support shaft 104 fixed to the carrier 103, and a bottom end portion of the friction wheel 105 is pressed against an output disk 106 fitted on the output shaft 101. . That is, the friction wheel 105 performs a planetary motion that rotates around the support shaft 104 while revolving around the output shaft 101. A non-rotatable transmission ring 107 is in contact with the outer peripheral surface of the friction wheel 105. When the contact position is moved in the axial direction, the rotation speed of the friction wheel 105 increases or decreases. Thereby, the ratio of the rotation speed of the bevel gear 102 and the output shaft 101 can be changed steplessly.

The output shaft 101 is provided with a loading device 108 that applies a pressing force in order to secure a frictional force between members that perform frictional transmission. As shown in FIG. 6B, the loading device 108 forms disc cams 106C and 109C on the output disk 106 and the gear 109 fixed to the output shaft 101, respectively, and is inserted into the hole of the guide member 110 therebetween. The ball body 111 is arranged. When the output shaft 101 rotates, the ball body 111 rides on the inclined portion X such as the disc cam 106C and pushes the output disk 106 to the left in the figure. The output disk 106 is not fixed to the output shaft 101 and is movable in the axial direction. When the output disk 106 moves leftward, the output disk 106 is pressed against the pressure contact portion between the lower end of the friction wheel 105 and the output disk 106. A force is applied, and a frictional force for power transmission is secured. This pressing force becomes larger as the torque of the output shaft 101 increases.
JP-A-3-9171 Japanese Utility Model Publication No. 39-33734 Japanese Patent Laid-Open No. 5-187509

  When power is transmitted using a friction wheel type continuously variable transmission, when the power (torque) to be transmitted is increased, the frictional force between the members performing frictional transmission increases. Excessive slipping may occur and cause slip damage. In order to prevent this, like a continuously variable transmission described in Patent Document 2, a pair of friction wheel continuously variable transmissions having the same structure and having a common input shaft are disposed opposite to each other symmetrically, A method of outputting by a single output shaft can be considered. According to this method, the frictional force between the members performing the frictional transmission is theoretically reduced to half and the axial thrust force acting on the input shaft during the frictional transmission is canceled out. The shaft support mechanism is simplified.

However, even if a pair of friction wheel type continuously variable transmissions of the same structure are arranged to face each other, each continuously variable transmission has inevitable manufacturing errors and assembly errors, and the lubrication conditions, etc. Since the wear due to aging changes depending on the difference, there is a slight difference in the output rotational speed of each continuously variable transmission when driven from a common input shaft. Since the two friction wheel type continuously variable transmissions are connected to a single output shaft, the rotational difference generated in each continuously variable transmission is absorbed by the slip generated between the members that perform friction transmission. However, this may increase the amount of slip and generate excessive heat in the continuously variable transmission, or may cause slip damage to any of the continuously variable transmissions. In addition, the same loading device that applies a pressing force between members that perform friction transmission needs to be provided for each friction wheel type continuously variable transmission.
The present invention provides a transmission device in which a pair of friction wheel type continuously variable transmissions are arranged so as to face each other, and prevents an increase in slippage due to a rotational difference between the respective continuously variable transmissions and provides a pressing force. It is an object of the present invention to solve the above problems by simplifying the configuration of the loading device.

In view of the above problems, the transmission of the present invention is a symmetrical arrangement of a pair of friction wheel continuously variable transmissions such that the output members of the respective friction wheel continuously variable transmissions are located in the center. A rolling element pressed against the output member is provided to allow relative rotational movement of both output members, and a pressing force is applied to the output member by the rolling element. That is, the present invention
"A transmission in which a pair of friction wheel type continuously variable transmissions having a common input shaft is arranged symmetrically with respect to a plane orthogonal to the input shaft,
An output member of each of the friction wheel type continuously variable transmissions is disposed to face an intermediate portion of the pair of friction wheel type continuously variable transmissions, and a radial direction is provided on an opposing surface of each of the output members. A circumferential groove having an inclined portion is formed on the outside,
Between the opposing surfaces of the output member, the rolling member is in contact with the inclined portion of each circumferential groove and rotates about a radial axis, and rotates about the axis of the input shaft, A guide member having a through space portion into which the rolling element is inserted; and
The guide member is connected to an output extraction member that takes out the output of each of the output members together,
Due to the relative displacement between each of the output members and the guide member, the rolling element moves radially outward and is pressed against the inclined portion of the circumferential groove formed in the output member. Press the output member in the opposite direction "
The transmission is characterized by this.

  According to a second aspect of the present invention, the rolling element inserted into the penetrating space portion is a sphere, and a linear portion is formed radially inward of the penetrating space portion so that the rolling element is the penetrating member. It can comprise so that it may move to radial direction outward with the movement of the circumferential direction in a space part.

  According to a third aspect of the present invention, the rolling element inserted into the through space is provided with a hemisphere and a shaft that are in contact with the inclined portion of the circumferential groove, and the rolling element The shaft is fitted into a rolling element support that contacts a radially inner corner of the through space, and the rolling element moves radially outward as the rolling element support inclines in the through space. It can be constituted as follows.

  In the transmission of the present invention, as described in claim 4, each of the friction wheel type continuously variable transmissions includes “a plurality of planetary wheels arranged around the input shaft, A rolling surface pressed against the input shaft and a speed change conical surface are formed. The ring-shaped output member is pressed against the outside of the rolling surface, and the speed change conical surface is Particularly advantageous effects are exhibited when the transmission ring is fixed in the rotational direction and movable in the axial direction.

  In the transmission of the present invention, a pair of friction wheel continuously variable transmissions having a common input shaft are disposed symmetrically, that is, opposed to a plane orthogonal to the input shaft. An output member of the friction wheel type continuously variable transmission is located at an intermediate portion between the two friction wheel type continuously variable transmissions. Between the two output members, a rolling element that contacts both output members and a guide member that holds the rolling element are arranged, and the output of the transmission is the output member of the two-friction type continuously variable transmission Are taken out through the guide member in a combined form. Therefore, the frictional force between the members that perform frictional transmission is halved and the axial thrust force that acts on the input shaft during frictional transmission is compared to that that shifts with a single friction wheel type continuously variable transmission. Since this cancels out, the structure of a thrust bearing or the like becomes simple.

  The rolling elements that are inserted into the through space portion of the guide member and disposed between the two output members move radially outward in accordance with relative displacement of the guide member with respect to the two output members. That is, as the guide member is relatively displaced rearward in the rotational direction of the output members due to the load torque acting on the output extraction member of the transmission, the rolling elements arranged between the output members are radially outward. Move to. A circumferential groove having an inclined portion radially outward is formed on the opposing surface of each output member, and the rolling elements that have moved radially outward are pressed against the inclined portions of both output members. As a result, the rolling element is locked between the inclined portion and the guide member, and power is transmitted from the output member of each friction wheel type continuously variable transmission to the guide member via the rolling element. The moving body acts to push both output members in opposite directions. Therefore, the rolling element disposed between the two output members also functions as a loading device shared by the two friction wheel type continuously variable transmissions, and the both friction wheel type continuously variable transmissions are provided via the respective output members. A pressing force is applied to the member, and a certain frictional force is generated between the members performing frictional transmission.

  In addition, the rolling elements inserted into the through space portion of the guide member are pressed by the radially outward inclined portions of both output members, but the rolling elements themselves can rotate around the radial axis. It is. Even if two friction wheel type continuously variable transmissions arranged opposite to each other have the same structure, the rotation of the output member in each continuously variable transmission due to inevitable manufacturing errors, assembly errors, etc. Although a slight difference occurs in the number, this difference in the rotation number can be absorbed by the rotation of the rolling element itself. In other words, the rolling element pressed by the inclined portion is subjected to a rotational moment due to the frictional force drawn by the output member having a high rotational speed and the frictional force dragged by the output member having a low rotational speed, and the rolling element is in the radial direction. Rotate around the axis to compensate for the rotational speed difference. In other words, the rolling element of the loading device according to the present invention allows a difference in rotational speed between the two output members, thereby causing slippage between the members performing frictional transmission due to the rotational speed difference between the two output members. Can be prevented.

  According to the second aspect of the present invention, the rolling element inserted into the through space is a sphere, and a linear portion is formed radially inward of the through space. When the guide member is displaced relative to both output members, the spherical rolling element moves the through space portion radially inward along the straight portion, and consequently moves radially outward. To come. According to this structure, since the structure of the penetration space part of a guide body and a rolling element is simple, the reliability at the time of an operation | movement is high, and it is possible to reduce manufacturing cost.

  According to a third aspect of the present invention, the rolling element inserted into the through space is configured by a hemisphere and a shaft that are in contact with the inclined portion of the circumferential groove of the output member, and the shaft of the rolling element is fitted. The rolling element support is provided in the through space, and both lower ends of the rolling element support are in contact with the radially inner corners of the through space. When the guide member is displaced relative to the two output members, the rolling element support body tilts in the penetrating space with the lower end as a fulcrum, and the rolling element moves radially outward. The portion is pressed against the inclined portion of the circumferential groove.

  The invention according to claim 4 is a transmission in which a pair of continuously variable transmissions that perform planetary transmission by a planetary wheel is opposed to the loading device in the present invention, that is, a friction wheel type continuously variable transmission. Is equipped with a plurality of planetary wheels arranged around the input shaft, and the planetary wheel is formed with a rolling surface pressed against the input shaft and a speed change conical surface. Is applied to a transmission in which a ring-shaped output member is press-contacted, and a speed-change conical surface is press-contacted with a speed-change ring that is fixed in the rotational direction and movable in the axial direction. is there. In such a friction wheel type continuously variable transmission, the output member can be stopped and reversed, and the speed change range is large.In addition, between the input shaft and the planetary wheel, between the output member and the planetary wheel, and between the transmission ring and the planetary wheel, Because of the fact that there are friction transmission parts at three locations between the two, there is a strong possibility that a difference in rotational speed will occur between the output members of the two friction wheel type continuously variable transmissions. Since the loading device according to the present invention allows a difference in the rotational speed to prevent an increase in slip between the friction transmission members, the effect when applied to a transmission equipped with this friction wheel type continuously variable transmission is as follows. , Especially big ones.

  Hereinafter, an embodiment of a transmission according to the present invention will be described with reference to the drawings. This embodiment relates to a transmission in which a pair of friction wheel type continuously variable transmissions that perform transmission by a planetary wheel are opposed to each other. First, the configuration of the continuously variable transmission, the shift principle, and the like will be described with reference to FIG. FIG. 1A is an overall sectional view of a planetary wheel type continuously variable transmission, and FIG. 1B is an equivalent model in which the continuously variable transmission is replaced with a planetary gear mechanism.

  As shown in FIG. 1A, in the planetary wheel type continuously variable transmission, a plurality of planet wheels 2 that perform planetary motion with respect to the input shaft 1 are arranged at equal intervals in the circumferential direction. The input shaft 1 includes input disks 11 and 12 having an outer periphery of a conical surface, and both end portions of the planetary wheel 2 also form conical surfaces 21 and 22, which serve as rolling surfaces for the input disk. ing. The planetary wheel 2 rotates around the central axis of the planetary wheel 2 while revolving around the input shaft 1 with the conical surface 21 pressed against the input disk 11 and the conical surface 22 pressed against the input disk 12. Therefore, the center axis of the planetary wheel 2 and the conical surfaces 21 and 22 at both ends and the conical surfaces of the input disks 11 and 12 are formed so as to intersect at one point of the axial extension portion of the input shaft 1 in the sectional view. The planet wheels 2 are connected to each other by a carrier 3 so that they can rotate and revolve.

  An output ring 4 that is an output member of the continuously variable transmission is pressed against the outer peripheral side of the conical surface 21 that is an end portion on the small diameter side of the planetary wheel 2. That is, the input disk 11, the conical surface 21 of the planetary wheel 2, and the output ring 4 correspond to the sun gear, the planetary gear, and the ring gear in the planetary gear mechanism, respectively.

  A speed change conical surface 23 is formed at the intermediate portion of the planetary wheel 2 and extends in the opposite direction to the conical surfaces at both ends. An outer straight line in the cross-sectional view of the transmission conical surface 23 is parallel to the axis of the input shaft 1, and the transmission ring 5 is pressed against the outer periphery thereof. The transmission ring 5 is configured to be constrained in the rotational direction and movable in the axial direction along the transmission cone surface 23. When the transmission ring 5 moves in the axial direction, the contact between the transmission ring 5 and the transmission cone surface 23 is achieved. Point P (pitch point) changes. Since the planetary wheel 2 rotates and revolves while rolling on the inner surface of the transmission ring 5 at the pitch point, the number of rotations thereof changes according to the radius at the pitch point of the transmission conical surface 23.

The number of rotations of each component of the planetary wheel type continuously variable transmission configured as described above is calculated using the equivalent model shown in FIG.
First, the rotation speed N5 of the ring gear B when the carrier is fixed and the ring gear B (corresponding to the transmission ring 5) rotates is obtained. If the radius of the sun gear (corresponding to the input disk 11) is R1, the rotational speed is N1, the radius of the planetary gear A (corresponding to the conical surface 21 of the planetary wheel 2) is R2, and the rotational speed is N2, N2 = −N1 × R1 / R2 (the direction of rotation of the sun gear is positive). Since the rotational speed of the planetary gear B (corresponding to the transverse section of the speed change conical surface 23 at the pitch point) is N2, the rotational speed N5 of the ring gear B is given by the following equation.
N5 = N2 × R3 / R5
R3: Radius of planetary gear B R5: Radius of transmission ring 5 Next, assuming that the radius of ring gear A (corresponding to output ring 4) meshing with the outside of planetary gear A is R4 and the rotational speed is N4, N4 = N2 × R2 / R4. However, this calculation is based on the assumption that the ring gear B rotates. Since the ring gear B is actually fixed, the rotational speed of each part is obtained by subtracting the rotational speed N5 of the ring gear B from the above rotational speed. Is required. The actual rotational speed No of the ring gear A is as shown in the following equation.
No = N4-N5 = N2 × (R2 / R4-R3 / R5)
Therefore, the ring gear A corresponding to the output ring 4 rotates in both the forward and reverse directions depending on the value of (R2 / R4-R3 / R5), and stops when this value becomes zero. Incidentally, if the actual input rotational speed is Ni, the gear ratio r is expressed by the following equation.
r = No / Ni = No / (N1-N5)

Here, an embodiment of the transmission of the present invention in which the above-described planetary wheel type continuously variable transmission is arranged to face each other will be described with reference to FIG.
In the transmission, a pair of planetary wheel type continuously variable transmissions A and B having the same structure are symmetrical with respect to a plane perpendicular to the common input shaft 1, and the output ring 4 is opposed at the intermediate portion. Are arranged as follows. However, the input disks 11 and 12 of the planetary wheel type continuously variable transmission B are fixed to both ends of a hollow sleeve connected to the input shaft 1 by a ball spline. Further, the rod 6 to which the transmission ring 5 is attached is provided with a reverse screw, and the transmission rings 5 of the planetary wheel type continuously variable transmissions A and B move the same distance in the opposite directions by the rotation of the rod 6. It is configured as follows.

  Between the output rings 4 of the planetary wheel type continuously variable transmissions A and B, a disc-shaped guide member 7 having a boss portion that is rotatably fitted to the input shaft 1 is installed. A continuous tooth 71 is formed on the outer periphery of the guide member 7, which meshes with a gear 81 fixed to the end of the output shaft 8 of the transmission, and outputs the planetary wheel type continuously variable transmissions A and B. It is an output extraction member that outputs to the outside together.

  A portion of the guide member 7 that faces each output ring 4 is provided with a through space 72 that penetrates the guide member 7, and the spherical rolling element 9 is inserted therein. As shown in FIG. 3A, the through space portion 72 is a space having a rectangular shape in which the radial outer side is an arc and the radial inner side is a straight line when viewed from the axial direction. When moving from the center to the left-right circumferential direction along the straight line on the radially inner side, as shown by the broken line, it will move radially outward. As shown in the enlarged cross-sectional view of FIG. 3B, the opposing surfaces of both output rings 4 are provided with circumferential grooves 42 having inclined portions 41 on the outer side in the radial direction in the cross section. Is displaced in the circumferential direction, the vicinity of the radially outer top portion of the rolling element 9 is pressed by the inclined portion 41 of each output ring 4. In other words, the rolling element 9 moves radially outward in accordance with the displacement in the circumferential direction and presses the inclined portion 41 of each output ring 4 in the opposite direction, so that the planetary wheel type continuously variable transmissions A and B It also functions as a loading device that generates a pressing force between members that perform friction transmission. Since the rolling element 9 is a sphere, when a difference occurs in the rotational speeds of both the output rings 4, the rolling element 9 can rotate around the radial axis and absorb the difference. The through space 72 into which the rolling element 9 is inserted does not have to be a straight line on the radially inner side, and as shown in FIG. The rolling element 9 moves radially outward along the circumferential movement of the through space 72.

  Next, the operation of the transmission shown in FIG. 2 will be described. When the input shaft 1 is rotated by power from an engine or the like, the input disks 11 and 12 of the planetary wheel type continuously variable transmissions A and B cause the plurality of planet wheels 2 to rotate and simultaneously revolve around the input shaft 1. Thereby, each output ring 4 pressed against the outer periphery of the end of the planetary wheel 2 rotates, and the number of rotations varies depending on the position of the transmission ring 5 pressed against the transmission conical surface 23 of the planetary wheel 2. As described above.

  Between the circumferential grooves 42 facing each output ring 4, the rolling elements 9 inserted in the through space 72 of the guide member 7 are placed. Since the load of the output shaft 8 of the transmission is acting on the guide member 7, when each output ring 4 rotates, the guide member 7 is relatively displaced rearward in the rotational direction with respect to the output ring 4. With the relative displacement of the guide member 7, the rolling element 9 moves in the circumferential direction along a straight line on the radially inner side of the through space 72 and moves outward in the radial direction to form the circumferential groove. Pressed by the inclined portion 41. Therefore, the rolling element 9 is in a locked state at that position, and the rotation of the output ring 4 is transmitted to the output shaft 8 via the rolling element 9 and the guide member 7. A reaction force corresponding to the load torque of the output shaft 8 is applied from the rolling element 9 to the inclined portion 41, and each output ring 4 is pressed in the opposite direction by this reaction force, and a pressing force is generated between the members that perform friction transmission. appear.

  By the way, even if the planetary wheel type continuously variable transmissions A and B have the same structure, the rotational speeds of both output rings 4 are somewhat different due to inevitable manufacturing errors. That is, the rotation of one output ring 4 is relatively fast and the rotation of the other output ring 4 is relatively slow with respect to the rotation of the guide member 7. When this rotational speed difference occurs, as shown in FIG. 4, there is a relative speed difference in the vicinity of the radially outer apex of the rolling elements 9 pressed by the inclined portions 41 of both output rings 4. A rolling moment based on the above acts, and the rolling element 9 rotates about the radial axis of the guide member 7. Due to this rotation, a difference in rotation speed between the two output rings 4 is allowed.

  As described above, the rolling elements 9 of the loading device of the present invention rotate in accordance with the difference in the number of rotations generated in the output rings 4 of the two continuously variable transmissions, so that each output ring 4 has the other output. The rotation is possible without being synchronized with the ring 4. Therefore, even if both the output rings 4 are connected to the common output shaft 8 via the guide member 7, an increase in slippage between the members that perform frictional transmission that occurs when the output ring 4 is forcibly synchronized. Can be avoided. When a difference occurs in the rotational speeds of both the output rings 4, the guide member 7 rotates at an average rotational speed of those rotational speeds.

  FIG. 5 shows a modification of the rolling element in the loading apparatus of the present invention. In this modification, the rolling element 9 includes a hemispherical body 91 and a shaft 92 that are in contact with the inclined portion of the circumferential groove 42 of each output ring 4, and the shaft 92 is attached to the rolling element support body 93 via a bearing. It is fitted so that it can rotate freely. As shown in FIG. 5 (a), the rolling element support 93 is a member having a trapezoidal cross section, and its bottom surface is placed on a straight line on the radially inner side in the through space 72 of the guide member 7, and both ends of the bottom surface. Is in contact with the corner Y of the through space 72.

When the guide member 7 is relatively displaced rearward in the rotational direction with respect to each output ring 4 due to the action of the load during power transmission, as shown in FIG. Is inclined with the corner Y as a fulcrum. As a result, the rolling element 9 moves radially outward and the hemisphere 91 is pressed against the inclined portion 41 of the circumferential groove, so that the rotation of the output ring 4 is output as in the case of the embodiment of FIG. While being transmitted to the shaft 8, the output rings 4 are pressed in directions opposite to each other, and a pressing force is generated between members performing frictional transmission. The speed difference generated between the output rings 4 is allowed by the rotation about the shaft 92 of the rolling element 9.
As can be seen from this modification, the rolling element 9 of the loading device according to the present invention has a relative relationship between the guide member and each output ring when power is transmitted from the input shaft of the transmission to the output shaft (output extraction member). In other words, any material that moves outward in the radial direction in the through space due to displacement can be used. The shape of the rolling element 9 is not limited to a sphere as long as it is a rotating body centered on the radial axis, and the inclined portion 41 of the circumferential groove 42 may be arcuate in cross section.

  As described above in detail, the present invention is a transmission in which a pair of friction wheel type continuously variable transmissions are arranged to face each other, and the output member of each friction wheel type continuously variable transmission is positioned at the center, A rolling element that is pressed by both output members is provided, and a pressing force is applied to both output members by the rolling element while allowing the relative rotational movement of both output members to function as a loading device for a friction wheel type continuously variable transmission. It is something to be made. In the above embodiment, a planetary wheel type continuously variable transmission is adopted as the friction wheel type continuously variable transmission in the transmission of the present invention, but a friction vehicle type continuously variable transmission such as a toroidal type continuously variable transmission is used. The loading device or the like of the present invention can be applied to a transmission in which a pair of toroidal continuously variable transmissions are arranged so as to face each other. Further, in the above embodiment, the output of the transmission is taken out by the gear, but there are various types of the embodiment such as taking out using the chain mechanism and moving the transmission ring by the link mechanism. Obviously changes are possible.

It is the figure which shows the schematic of the structure of the planetary wheel type continuously variable transmission used for this invention, and an equivalent model. It is a figure which shows the structure of the transmission of this invention. It is a figure which shows the loading apparatus of this invention. It is a figure explaining the action | operation of the loading apparatus of this invention. It is a figure which shows the modification of the rolling element in the loading apparatus of this invention. It is a figure which shows the structure of the conventional planetary wheel type continuously variable transmission, and its loading apparatus.

Explanation of symbols

1 Input shaft 2 Planetary wheel 23 Speed change conical surface 3 Carrier 4 Output ring (output member)
41 Inclined portion 5 Transmission ring 7 Guide member 72 Through space portion 8 Output shaft (output extraction member)
9 Rolling elements

Claims (4)

A transmission in which a pair of friction wheel type continuously variable transmissions having a common input shaft are arranged symmetrically with respect to a plane orthogonal to the input shaft,
An output member of each of the friction wheel type continuously variable transmissions is disposed to face an intermediate portion of the pair of friction wheel type continuously variable transmissions. A circumferential groove having an inclined portion is formed on the outside,
Between the opposing surfaces of the output member, the rolling member is in contact with the inclined portion of each circumferential groove and rotates about a radial axis, and rotates about the axis of the input shaft, A guide member having a through space portion into which the rolling element is inserted; and
The guide member is connected to an output extraction member that takes out the output of each of the output members together,
Due to the relative displacement between each of the output members and the guide member, the rolling element moves radially outward and is pressed against the inclined portion of the circumferential groove formed in the output member. The transmission is characterized by pressing the output member in the opposite direction. The rolling element inserted into the penetrating space is a sphere, and a linear portion is formed radially inward of the penetrating space, and the rolling element is circumferential in the penetrating space. The transmission according to claim 1, which moves radially outward as it moves. The rolling element inserted into the penetrating space includes a hemisphere that contacts the inclined portion of the circumferential groove and a shaft, and the axis of the rolling element is radially inward of the penetrating space. 2. The transmission according to claim 1, wherein the transmission is fitted into a rolling element support in contact with a corner, and the rolling element moves radially outward as the rolling element support inclines in the through space. Each of the friction wheel type continuously variable transmissions includes a plurality of planetary wheels arranged around the input shaft, and the planetary wheels include a rolling surface pressed against the input shaft, a transmission cone surface, The ring-shaped output member is pressed against the outside of the rolling surface, and the speed change conical surface is fixed in the rotational direction and movable in the axial direction. The transmission according to any one of claims 1 to 3, wherein is pressure-contacted.

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