JP2006097825A - Toroidal type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact toroidal type continuously variable transmission. <P>SOLUTION: This toroidal type continuously variable transmission is provided with a toroidal type variator 4, a mechanical loading mechanism 12, a two-input type planetary gear mechanism 16 in which rotation from the variator is transmitted, a power direct connection transmission mechanism 15 for transmitting the rotation of an output disc into an input part on one side of the planetary gear mechanism, power circulation transmission mechanisms 9, 10 each transmitting the rotation of a variator input shaft into an input part on the other side of the planetary gear mechanism by bypassing the variator, and an output shaft for taking out the output rotation of the planetary gear mechanism. The toroidal type variator, the planetary gear mechanism, and the output shaft are arranged in this order from a driving source. The mechanical loading mechanism is arranged between the toroidal type variator and the planetary gear mechanism. The variator input shaft passes through an input disc and the output disc and comes into contact with the mechanical loading mechanism continuously. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a toroidal continuously variable transmission, and more particularly to a power split toroidal continuously variable transmission.

  An example of a toroidal continuously variable transmission used as a conventional automobile transmission is an input shaft connected to an engine, an input disk connected to the input shaft, an output disk, and tiltable between the input disk and the output disk. A double-cavity toroidal variator composed of a power roller arranged on the power supply, a power transmission mechanism for transmitting the output of the variator to a planetary gear mechanism having two degrees of freedom using a counter shaft, and bypassing the variator from the input shaft. And a bypass shaft that directly transmits power to a planetary gear mechanism having two degrees of freedom, and an output shaft that is connected to the planetary gear mechanism and transmits power to a driving wheel (not shown) (see Patent Document 1). .

  In this toroidal continuously variable transmission, two power transmission modes are configured according to the restraint state of the planetary gear mechanism. The first mode is a mode in which the counter shaft directly transmits power to the output shaft by interlocking the planetary gear mechanism having two degrees of freedom.

In the second mode, the planetary gear mechanism having two degrees of freedom is released from the interlock in the first mode, so that the power circulated from the planetary gear mechanism to the variator is added to the input from the engine and bypassed. In this mode, the planetary gear mechanism flows through the shaft, and the output shaft outputs the difference between the flowed power and the power circulated through the output shaft.
Japanese Patent Laid-Open No. 11-63147

  However, since the power transmitted by the bypass shaft is the sum of the power circulated from the planetary gear mechanism to the variator and the input from the engine as described above, there is a problem that the shaft diameter increases.

  The arrangement of the bypass shaft having a large shaft diameter is disclosed in FIGS. 1, 3 and 7 of Patent Document 1. In FIG. 1, the bypass shaft is disposed coaxially with the counter shaft via a gear mechanism from the front portion of the mechanical loading mechanism disposed between the double cavity type toroidal variator and the power source. However, there is a problem that not only is it complicated and expensive, but installation space is also increased.

  In FIG. 3, the bypass shaft is arranged coaxially with the variator shaft. However, since the bypass shaft having a large shaft diameter penetrates the center of the input / output disk, there is a problem that the outer diameter of the input / output disk increases.

  In FIG. 7, there is an advantage that the bypass shaft is simplified by disposing the mechanical loading mechanism between the two sets of toroidal cavities. On the other hand, by using the two sets of mechanical loading mechanisms, the mechanism is In addition to being complicated and costly, there is a problem that installation space is also increased.

  The present invention has been made paying attention to the above circumstances, and an object of the present invention is to provide a toroidal-type continuously variable transmission that has a simple mechanism and is inexpensive.

  A first aspect of the present invention is a variator input shaft connected to a drive source, two sets of input disks, two sets of output disks, and a tiltable arrangement between the input disks and the output disks. A toroidal variator that changes the rotational speed of the variator input shaft, a mechanical loading mechanism that presses the input disk toward the output disk through the power roller, and the variator A two-input planetary gear mechanism that transmits the rotation of the output disk, a power direct transmission mechanism that transmits the rotation of the output disk to one input portion of the planetary gear mechanism, and the variator bypassing the rotation of the variator input shaft And a power circulation transmission mechanism for transmitting to the other input part of the planetary gear mechanism, and an output shaft for taking out the output rotation of the planetary gear mechanism. In the toroidal continuously variable transmission, the toroidal variator, the power circulation transmission mechanism, the planetary gear mechanism, and the output shaft are arranged in this order from the drive source, and the mechanical loading mechanism is arranged between the toroidal variator and the power circulation. The variator input shaft is connected to the mechanical loading mechanism through the input disk and the output disk, and the mechanical loading mechanism and the power circulation transmission mechanism are connected to each other. It is characterized by that.

  According to the first invention, the mechanical loading mechanism 12 is disposed on the input disk 5 side opposite to the engine side, and the variator input shaft 3 is passed through the input disk shaft, thereby transmitting a large amount of power. The bypass shaft 13 can be shortened to suppress an increase in weight and the like, and an increase in the outer diameter of the input disk 5 and the output disk 7 can be suppressed. Further, the number of mechanical loading mechanisms 12 can be reduced to one, and the entire continuously variable transmission can be made compact. (Effects corresponding to Claim 1) Since the mechanical loading mechanism and the planetary gear mechanism are adjacent to each other, the connecting shaft can be simplified, and the variator input shaft passes through the input / output disk. Therefore, an increase in the diameter of the input / output disk is suppressed. Thereby, cost reduction and size reduction of a continuously variable transmission can be achieved.

  FIG. 1 shows a system diagram of a power split type continuously variable transmission. An input shaft 1 connected to a drive source 100 such as an engine is connected to a variator input shaft 3 and a mechanical loading mechanism such as a loading cam 12 via a starting device 2 such as a torque converter. Power is transmitted to a double cavity type toroidal variator (hereinafter simply referred to as a variator) 4 through the mechanical loading mechanism 12. The variator 4 is installed between the drive source and the mechanical loading mechanism 12. The variator 4 is provided with a pair of opposed input disks 5 that rotate in conjunction with the variator input shaft 3. The input disk shaft 6 to which the input disk 5 is fixed is a hollow shaft installed on the same center line as the variator input shaft 3 and is configured to be rotatable with respect to the variator input shaft 3. A pair of output disks 7 is installed between the pair of input disks 5, and the output disk 7 is fixed to the output disk shaft 7a. The output disk shaft 7 a is a hollow shaft installed on the same center line as the input disk shaft 6 described above, and is formed to be rotatable with respect to the input disk shaft 6. Further, an output gear 7b is fixed to the output disk shaft 7a, and the output gear 7b meshes with a counter input gear 10a fixed to a counter shaft 10 described later. Here, the output gear 7 b and the counter input gear 10 a are used as the first power transmission mechanism 9. The input disk 5 and the output disk 7 are connected via a plurality of power rollers 8 that are in rolling contact with both disks, and the rotation of the input disk is transmitted to the output disk. The power roller 8 installed between the input disk 5 and the output disk 7 is provided so as to be tiltable. By changing the tilt angle of the power roller 8, the speed ratio between the input disk 5 and the output disk 7 can be changed. Control.

  The mechanical loading mechanism 12 is further connected to a bypass shaft 13 coaxially with the variator input shaft 3, and the bypass shaft 13 is connected to the third power transmission mechanism 15. The third power transmission mechanism 13 includes a set of planetary gear mechanisms, and the rotation of the bypass shaft 13 is transmitted to the ring gear 15r. The power transmitted to the ring gear 15r is transmitted to the planetary gear mechanism 16 from the carrier 15c that supports the planetary gear 15p. The sun gear 15 s of the planetary gear mechanism that constitutes the third power transmission mechanism 15 is connected to the bypass clutch 14, and the power transmission to the planetary gear mechanism is controlled according to the engagement state of the clutch 14. Here, the gear ratio of the third power transmission mechanism 15 is set to 1: 1, that is, the input rotation speed and the output rotation speed are set to be the same.

  The planetary gear mechanism 16 will be described. The planetary gear mechanism 16 includes a sun gear 16a having an output shaft 19, a plurality of planetary gears 16b meshing with the output shaft 19, a carrier 16c coupling the planetary gears, and a ring gear 16d meshing with the planetary gear 16b. The ring gear 16 d is connected to the carrier 15 c of the third power transmission mechanism 15. Further, a reverse brake 17 that allows and restrains the rotation of the ring gear 16d is provided between the ring gear 16d and the planetary gear mechanism 16 housing.

  The sun gear 16 a of the planetary gear mechanism 16 (planetary gear mechanism) is connected to the output shaft 19, while the carrier 16 c is connected to the output shaft 19 via the forward clutch 18. A gear 11a is fixed between the carrier 16c and the forward clutch 18, and is connected to a counter output gear 10b fixed to an end of the counter shaft 10 via a counter gear 11b. Here, the gear 11 a, the counter gear 11 b, and the counter output gear 10 b constitute the second power transmission mechanism 11. The first power transmission mechanism 9, the second power transmission mechanism 11, and the forward clutch 18 constitute a power direct transmission mechanism, and the bypass shaft 13, the bypass clutch 14, and the third power transmission mechanism 15 are power circulation transmission. Configure the mechanism.

  It is comprised in this way, Next, an effect | action is demonstrated.

  When the variator input shaft 3 is stopped with the engine rotating, the variator 4 is at the maximum deceleration position, the bypass clutch 14 and the reverse brake 17 are in the released state, and the forward clutch 18 is in the engaged state. To do. From this state, when the variator input shaft 3 is started to rotate in a predetermined direction by the action of the starting device 2, the input disk 5 of the variator 4 is moved by the action of the mechanical loading mechanism 12 along with the rotation of the variator input shaft 3. It rotates at the same rotational speed in the same direction as the variator input shaft 3. At this time, the rotation of the input disk 5 is transmitted to the output disk 7 via the power roller 8. Further, the rotation of the output disk is transmitted to the output shaft 19 via the first power transmission mechanism 9, the counter shaft 10, the second power transmission mechanism 11, and the forward clutch 18. Here, since the power roller 8 is at the maximum deceleration position as described above, it is transmitted to the output shaft 19 so as to rotate in a predetermined direction and to rotate at a lower speed than the input shaft 1. This power transmission mode is defined as a first mode.

  When the power roller 8 is tilted and the variator 4 is shifted to the speed increasing side while maintaining the first mode, the rotational speed of the output shaft 19 increases, and the speed ratio of the toroidal type continuously variable transmission is increased. To increase.

  Next, considering the case where the bypass clutch 14 is engaged and the forward clutch 18 and the reverse brake 17 are released, the transmission direction of the power passing through the variator 4 is opposite to that in the first mode, that is, the variator input shaft 3. , And the circulating power transmitted from the input disk 5 through the variator 4 through the mechanical loading mechanism 12 is added together and transmitted to the bypass shaft 13. Here, the power that flows back through the variator 4 is input to the output disk 7 through the rotation of the carrier 16 c of the planetary gear mechanism 16 through the second power transmission mechanism 11, the counter shaft 10, and the first power transmission mechanism 9. Is.

  The power transmitted to the bypass shaft 13 is transmitted to the ring gear 16 d of the planetary gear mechanism 16 through the third power transmission mechanism 15. Part of the power transmitted to the ring gear 16d is transmitted to the output shaft 19 via the sun gear 16a, and the rest is transmitted to the carrier 16b, the second power transmission mechanism 11, the counter shaft 10, and the first power transmission mechanism as described above. 9 and then flows into the output disk 7 of the variator 4. In this state, when the gear ratio of the variator 4 is shifted to the speed reduction side, the rotation of the carrier 16b of the planetary gear mechanism 16 decreases, and as a result, the sun gear 16a, that is, the output shaft 19 is accelerated. This power transmission mode is defined as a second mode.

  Next, when the output shaft 19 is reversely rotated to reverse the vehicle, the bypass clutch 14 and the forward clutch 18 are released, and the reverse brake 17 is engaged. As a result, the ring gear 16d of the planetary gear mechanism 16 is fixed, and the planetary gear 16b revolves around the sun gear 16a while meshing with the ring gear 16d and the sun gear 16a. Therefore, the sun gear 16a and the output shaft 19 fixed to the sun gear 16a rotate in the opposite direction to the mode described above.

  According to the first embodiment described above, the mechanical loading mechanism 12 is disposed on the input disk 5 side opposite to the engine side, and the variator input shaft 3 is passed through the input disk shaft 6. The bypass shaft 13 for transmitting large power can be shortened to suppress an increase in weight and the like, and an increase in the outer diameter of the input disk 5 and the output disk 7 can be suppressed. In addition, the number of mechanical loading mechanisms 12 can be reduced to one, and the entire continuously variable transmission can be made compact (effect corresponding to claim 1).

  In the present embodiment, the third power transmission mechanism 15 is constituted by a planetary gear, but it goes without saying that the same effect can be obtained by a parallel shaft gear.

  FIG. 2 is a diagram showing a detailed structure around the third power transmission mechanism 15. The variator input shaft 3, the support portion 12 a of the mechanical loading mechanism 12, and the bypass shaft 13 are integrally formed as a shaft 101, and this shaft 101 is an inner wall of a transmission case 102 in which a continuously variable transmission is accommodated. An intermediate wall 103 extending inward from the inner wall is rotatably supported via a bearing 104. The intermediate wall 103 is formed between the mechanical loading mechanism 12 and the third power transmission mechanism 15.

  A ring gear 15r of a planetary gear mechanism that constitutes the third power transmission mechanism 15 is connected to the bypass shaft 13 via a connecting plate 105. The sun gear 15s is spline-fitted to the hub member 106, and the driven plate 14a of the bypass clutch 14 is spline-fitted to the external teeth of the hub member 106. The driven plate 106a engages with the drive plate 14b fitted in the spline groove on the inner wall of the extension case 107 fixed to the transmission case 102 in the bypass axial direction. A piston 108 for controlling the engagement is provided so as to be movable in the bypass axis direction, and the piston 108 presses the drive plate 14b. The body portion 108 a of the piston 108 is accommodated in a cylinder chamber 109 formed in an annular groove shape on the intermediate wall 103. The hydraulic fluid is supplied from the oil passage 102a formed in the transmission case 102 to the gap between the bottom surface 109a of the cylinder chamber 109 and the piston body 108a, the piston 108 moves in the direction of the bypass shaft 13, and the friction member 106a and the friction plate 107a. And engage. The sun gear 15 s is fixed by the engagement of the bypass clutch 14. A spring retainer 110 is provided on the opening side of the cylinder chamber 109, and a spring that urges the piston 108 toward the bottom surface 109 a of the cylinder chamber 109 is installed between the piston body 108 a and the spring retainer 110. When the hydraulic oil pressure is low, the piston 108 is moved in the direction of the bottom surface 109a, and the bypass clutch 12 is disengaged.

Therefore, in the present invention, the bypass clutch 14 of the power circulation transmission mechanism is disposed on the mechanical loading mechanism 12 side, and the bypass axial direction from the transmission case 102 is provided between the mechanical loading mechanism 12 and the third power transmission mechanism 15. Since the intermediate wall 103 extending to the intermediate wall 103 and the hydraulic oil passage for the piston 108 for controlling the engagement of the bypass clutch 14 are formed in the intermediate wall 103, the following effects are obtained.
The oil passage of the bypass clutch 14 can be easily formed, and the oil passage can be easily routed. In addition, since the hydraulic oil can be supplied without using the rotating member, the friction does not increase (effect corresponding to claim 2).

  FIG. 3 shows a second embodiment, and the same components as those of the first embodiment shown in FIG. In the present embodiment, the third power transmission mechanism 15 constituted by a planetary gear mechanism is eliminated, and the bypass shaft 13 is connected to the ring gear 16d of the planetary gear mechanism 16 (planetary gear mechanism) via the bypass clutch 14. That is, by eliminating the third power transmission mechanism 15, further cost reduction and compactness of the entire transmission can be achieved. In the present embodiment, the first power transmission mechanism 9, the second power transmission mechanism 11 and the forward clutch 18 constitute a power direct transmission mechanism, and the bypass shaft 13 and the bypass clutch 14 serve as a power circulation transmission mechanism. Constitute.

  FIG. 4 is a diagram showing a detailed structure around the power circulation transmission mechanism and the planetary gear mechanism of the second embodiment. Compared with the structure shown in FIG. 2, the power transmission path of the planetary gear mechanism 16 (planetary gear mechanism) is different. Specifically, the sun gear 16a is spline fitted to the output shaft 19, the carrier 16c is connected to the second power transmission mechanism 11, and the ring gear 16d is coupled to the drum 111 and provided on the outer periphery of the drum 111. It is fixed to the extension case 107 by the band brake 17.

  On the other hand, the bypass shaft 13 is supported by an intermediate wall 103 extending from the transmission case 102 via a bearing 104. The intermediate wall 103 is formed with an extension portion 103b extending toward the bypass shaft 13 and an annular portion 103a extending in parallel with the bypass shaft 13 toward the planetary gear mechanism 16 side. The bearing 104 is installed between 13 outer diameters. The inner cylindrical portion 111a of the drum 111 is rotatably supported on the outer diameter portion of the annular portion 103a. Further, the drum 111 is constituted by an outer cylinder portion 111b to which the ring gear 16d is fixed, and a vertical wall 111c connecting the outer cylinder portion 111b and the inner cylinder portion 111a. In the drum 111, an annular member 112 extending in the direction of the planetary gear mechanism 16 is fixed to the vertical wall 111c. A piston 113 that slides in the bypass axis direction is installed between the outer diameter portion of the inner cylinder portion 111 a of the fixing member 111 and the annular member 112. A cylinder chamber 114 for moving the piston 113 is formed between the piston 113 and the vertical wall 111 c of the drum 111, and an oil passage 115 for supplying hydraulic oil to the cylinder chamber 114 inside the inner cylinder portion 111 a and the intermediate wall 103. Is formed.

  The piston 113 controls the engagement state of the fixed driven plate 106 a that is spline-fitted to the hub member and the drive plate 111 d that is spline-fitted to the inner surface of the outer cylinder portion 111 b of the drum 111. The driven plate 106a, the drive plate 111d, and the piston 113 form the bypass clutch 14.

  Therefore, even this configuration has the same effects as those of the first embodiment. That is, according to the first embodiment described above, the mechanical loading mechanism 12 is disposed on the input disk 5 side opposite to the engine side, and the variator input shaft 3 is passed through the input disk shaft 6. As a result, the bypass shaft 13 for transmitting large power can be shortened, and an increase in weight and the like can be suppressed, and an increase in the outer diameter of the input disk 5 and the output disk 7 can be suppressed. In addition, the number of mechanical loading mechanisms 12 can be reduced to one, and the entire continuously variable transmission can be made compact (effect corresponding to claim 1).

  Further, the bypass clutch 14 is disposed on the mechanical loading mechanism 12 side of the third power mechanism 15, and between the mechanical loading mechanism 12 and the third power transmission mechanism 15 from the transmission case 102 to the bypass axial direction. The intermediate wall 103 is formed so as to support the variator input shaft 3 and the bypass shaft 13 with the intermediate wall 103, and the hydraulic oil passage of the piston 113 that controls the engagement of the bypass clutch 14 is provided in the intermediate wall 103. The oil passage of the hydraulic oil passage of the bypass clutch 14 can be shortened, and the oil passage can be easily routed. In addition, since the hydraulic oil can be supplied without using the rotating member, the friction does not increase (effect corresponding to claim 2).

  The present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea of the present invention.

  The continuously variable transmission to which the present invention is applied can be miniaturized and is useful for vehicles equipped with a continuously variable transmission.

BRIEF DESCRIPTION OF THE DRAWINGS The block diagram of the toroidal type continuously variable transmission in 1st Embodiment of this invention. The detailed structure figure around the 3rd power transmission mechanism. The block diagram of the toroidal type continuously variable transmission in 2nd Embodiment. The detailed structure figure around the 3rd power transmission mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Input shaft 2 ... Starting device 3 ... Variator input shaft 4 ... Double cavity type toroidal variator 5 ... Input disc 6 ... Input disc shaft 7 ... Output disc 7a ... Output disc shaft 8 ... Power roller 9 ... First power transmission Mechanism 10 ... Counter shaft 10a ... Counter input gear 10b ... Counter output gear 11 ... Second power transmission mechanism 12 ... Mechanical loading mechanism 13 ... Bypass shaft 14 ... Bypass clutch 15 ... Third power transmission mechanism 16 ... Planetary gear mechanism 17 ... Reverse clutch 18 ... Forward clutch 19 ... Output shaft 100 ... Engine 101 ... Shaft 102 ... Transmission case 103 ... Intermediate wall 104 ... Bearing 105 ... Drum 106 ... Hub member 107 ... Extension case 108 ... Piston 109 ... Cylinder chamber 110 ... Return spring

Claims (2)

A variator input shaft connected to the drive source;
It consists of two sets of input disks, two sets of output disks, and a plurality of power rollers that are tiltably disposed between the input disks and the output disks, and changes the rotational speed of the variator input shaft. Toroidal variator,
A mechanical loading mechanism for pressing the input disk toward the output disk through the power roller;
A two-input planetary gear mechanism to which rotation from the variator is transmitted;
A direct power transmission mechanism for transmitting rotation of the output disk to one input portion of the planetary gear mechanism;
A power circulation transmission mechanism that transmits the rotation of the variator input shaft to the other input portion of the planetary gear mechanism, bypassing the variator;
An output shaft for taking out the output rotation of the planetary gear mechanism;
Toroidal continuously variable transmission with
The toroidal variator, the power circulation transmission mechanism, the planetary gear mechanism, and the output shaft are arranged in this order from the drive source, and the mechanical loading mechanism is arranged between the toroidal variator and the power circulation mechanism,
A toroidal type characterized in that the variator input shaft passes through the input disk and the output disk and is connected to the mechanical loading mechanism, and the mechanical loading mechanism and the power circulation transmission mechanism are connected. Continuously variable transmission. The power circulation transmission mechanism includes friction engagement means for releasing engagement of a predetermined rotating member of the power circulation transmission mechanism with another member by an operation of a hydraulic piston, the planetary gear mechanism, and the machine. A bypass shaft that transmits power to the loading mechanism,
A support wall for supporting the bypass shaft via a bearing is provided between the mechanical loading mechanism and the power circulation transmission mechanism,
The toroidal continuously variable transmission according to claim 1, wherein a hydraulic oil passage of a hydraulic piston of the friction engagement means is provided in the support wall.

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