JP4712593B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission suitable for use in an automobile, and more particularly to a continuously variable transmission including a planetary gear mechanism that rotationally combines an input shaft rotation and a continuously variable rotation of a toroidal continuously variable transmission. .

  2. Description of the Related Art Conventionally, a continuously variable transmission using a toroidal-type continuously variable transmission and uniaxially arranged members has been proposed (Patent Document 1). The continuously variable transmission combines a toroidal continuously variable transmission (variator) and a planetary gear device, and synthesizes the rotational rotation of the toroidal continuously variable transmission and the input rotation from the input shaft while circulating torque, It has a low mode that reverses and decelerates and outputs the combined rotation, and a high mode that outputs the combined rotation as it is, and obtains an appropriate forward / reverse speed rotation as an output rotation of an automobile including gear neutral (GN). (IVT; infinitely variable transmission).

  The uniaxial continuously variable transmission includes an input disk, an output disk, and a toroidal continuously variable transmission that includes a roller that is disposed between the two disks and can change a contact radius position between the two disks. A planetary gear mechanism having a carrier in which the first, second, and third pinions (three-step pinions) are arranged in the axial direction in turn, and a reversing gear mechanism having a carrier in which the fourth and fifth pinions are arranged in the axial direction; A connecting member that connects the third sun gear meshing with the third pinion and the input-side sun gear of the reverse gear mechanism, and a low brake and planetary gear second sun gear that can stop the output-side sun gear of the reverse gear mechanism (high mode) And a low / high switching mechanism comprising a high clutch interposed between the hour output gear) and the output shaft.

  As a result, the continuously variable transmission is reversed and shifted through the carrier and the continuously variable transmission that directly inputs the rotation of the input shaft in the low mode in which the low brake is engaged and the high clutch is released. The rotation of the first sun gear is combined and decelerated by the planetary gear mechanism and output to the third sun gear, and further, the rotation of the output gear is input to the reversing gear mechanism via the connecting member. The rotation is reversed and output to the output shaft. In the high mode in which the low brake is released and the high clutch is engaged, the rotation of the second sun gear is transmitted to the output shaft via the high clutch.

  On the other hand, a toroidal continuously variable transmission is used, which is composed of a biaxial transmission path that outputs the rotation of the output disk via a countershaft (counter shaft). A continuously variable transmission (Patent Document 2) that combines torque and the input rotation from the input shaft by torque circulation and a continuously variable transmission (Patent Document 3) that combines by torque circulation in the high mode have been proposed.

  Among the above biaxial continuously variable transmissions, those that circulate in the low mode are the toroidal continuously variable transmission (half toroidal type) similar to the above and the output disk of the toroidal continuously variable transmission on the outer peripheral side. A counter shaft for transmitting the speed change rotation of the output disk on an axis parallel to the input shaft, a planetary gear having a sun gear, a carrier, and a ring gear, and the rotation of the input shaft can be freely input to the carrier. And a high clutch that integrally engages the carrier and the ring gear.

  Thus, in the continuously variable transmission in the low mode where the low clutch is engaged and the high clutch is released, the rotation of the input shaft is directly input via the continuously variable transmission and the counter shaft ( The rotation of the sun gear that has been shifted (reversed by the continuously variable transmission and re-reversed by the counter gear) is synthesized and decelerated by the planetary gear, output to the ring gear, and output from the ring gear to the output shaft. In the high mode in which the low brake is released and the high clutch is engaged, the variable speed rotation of the continuously variable transmission is input only to the sun gear via the counter shaft, and the rotation of the sun gear is integrated by the engagement of the high clutch. It is output to the output shaft through the rotating planetary gear.

  Among the above biaxial continuously variable transmissions, those that circulate in torque in the high mode are the same as those described above on the toroidal continuously variable transmission (half toroidal type) and the output disk of the toroidal continuously variable transmission. A countershaft meshing on the outer periphery and transmitting the speed change rotation of the output disk on an axis parallel to the input shaft; a first sun gear connected to the countershaft; a connected first carrier; A planetary gear mechanism having a second ring gear, a connected first ring gear and a second carrier, a low brake capable of fixing the rotation of the second sun gear, and a rotation of the input shaft to be input to the first carrier. And a high clutch.

  Thus, in the continuously variable transmission, in the low mode in which the low clutch is engaged and the high clutch is released, the rotation of the first sun gear that is reversed and shifted through the continuously variable transmission and the countershaft. Are combined and decelerated by the planetary gear mechanism, output to the first ring gear and the second carrier, and output to the output shaft. In the high mode in which the low brake is released and the high clutch is engaged, the rotation of the first sun gear and the rotation of the input shaft are input via the counter shaft. The rotation of the first carrier is synthesized by the planetary gear mechanism and output from the first ring gear to the output shaft.

  In this continuously variable transmission, the reverse rotation of the first carrier is fixed by the reverse brake, and the variable speed rotation of the continuously variable transmission input to the first sun gear is reversed to output the output shaft from the first ring gear. Is output.

International Publication No. WO03 / 100275A1 JP 11-63148 A JP 2004-144300 A

  By the way, the uniaxial continuously variable transmission uses the planetary gear mechanism to synthesize the above-mentioned variable speed rotation and input rotation by torque circulation, and the combined rotation is used as a high mode output. A gear that reverses and decelerates (a third pinion, a third sun gear, a reverse gear mechanism, etc.) is required. For this reason, it is difficult to shorten the axial direction, which has hindered the compactness of the continuously variable transmission in the axial direction.

  On the other hand, in the above-described biaxial continuously variable transmission, only one of the low mode and the high mode performs torque circulation in the planetary gear mechanism, thereby forming different gear ratios and reverse states. It is not necessary to provide a reverse gear mechanism or the like, and the continuously variable transmission in the axial direction can be made compact.

  However, since the variable speed rotation of the continuously variable transmission is transmitted using the countershaft in both the low mode and the high mode, it is necessary to transmit a rotation with a large reduction ratio, particularly in the low mode. Since it is necessary to transmit a large torque, there is a problem in that the durability of the countershaft and the bearing that rotatably supports the countershaft is prevented from being improved. Further, in order to improve the strength and durability of the countershaft, it is necessary to increase the diameter of the countershaft or enlarge the rotation support member such as the bearing. For this reason, the continuously variable transmission is prevented from being made compact.

  Furthermore, since the planetary gear mechanism receives the variable speed rotation of the continuously variable transmission regardless of whether in the low mode or the high mode, the number of teeth of each gear is limited to the number of teeth corresponding to both modes. As a result, the sun gear diameter, the pinion diameter, the ring gear diameter, and the like are limited, leading to enlargement of the planetary gear mechanism, which hinders downsizing the continuously variable transmission particularly in the radial direction.

  Therefore, the present invention includes a second transmission shaft that can transmit continuously variable speed rotation of the output disk of the toroidal type continuously variable transmission device to the output shaft by bypassing the planetary gear mechanism, thereby improving durability and downsizing. An object of the present invention is to provide a continuously variable transmission.

According to the first aspect of the present invention (see, for example, FIGS. 1 to 7 ), an input shaft (2) connected to a driving source, and the input shaft (2) are disposed on the input shaft (2). the input disk (11A, 11B) which rotation is input and a rotation to shift the continuously variable rotation (Vout) output disks (12A, 12B) toroidal type continuously variable transmission is output from (10), a planetary gear mechanism ( 30), a low / high switching mechanism (20) capable of switching between the low mode and the high mode according to the engagement state of the low engagement element (L) and the high engagement element (H), and connected to the drive wheel. In the continuously variable transmission (1) having an output shaft (3),
A first transmission shaft (71) for transmitting continuously variable speed rotation (Vout) of the output disk (12A, 12B) to the planetary gear mechanism (30);
A second transmission shaft (75, 175, 275) capable of transmitting continuously variable speed rotation (Vout) of the output disk (12A, 12B) to the output shaft (3) by bypassing the planetary gear mechanism (30); With
In the low mode, the rotation of the input shaft (2) and the continuously variable speed rotation (Vout) of the first transmission shaft (71) are rotationally synthesized by the planetary gear mechanism (30) and the output shaft ( 3)
In the high mode, the continuously variable speed rotation (Vout) is transmitted to the output shaft (3) via the second transmission shaft (75, 175, 275).
The continuously variable transmission (1) is characterized by the above.

According to the second aspect of the present invention (see, for example, FIGS. 1 to 5), the second transmission shaft has an input gear (73) fixed to one end and an output gear (76) fixed to the other end. And a counter shaft (75) disposed on an axis parallel to the input shaft (2),
A continuously variable output gear (which rotates at the continuously variable speed rotation (Vout) in conjunction with the output disk (12A, 12B) and meshes with the input gear (73) of the counter shaft (75) at least in the high mode. 72)
An output shaft interlocking gear (78) interlocked with the output shaft (3) at least in the high mode;
An output gear (76) of the counter shaft (75) and a reversing gear (77) meshing with the output shaft interlocking gear (78);
Lying in the continuously variable transmission (1 ₁₎ of claim 1, wherein.

According to the third aspect of the present invention (see, for example, FIGS. 6 and 7), the second transmission shaft has an input member (174) fixed to one end and an output gear (176) fixed to the other end. And a counter shaft (175) disposed on an axis parallel to the input shaft (2).
A continuously variable output member (172) capable of rotating at the continuously variable speed rotation (Vout) in conjunction with the output disk (12A, 12B);
A belt-like member (173) wound around the stepless rotation output member (172) and the input member (174) of the counter shaft (175);
An output shaft interlocking gear (178) meshing with the output gear (176) of the counter shaft (175) and interlocking with the output shaft (3) at least in the high mode.
Lying in the continuously variable transmission (1 ₂₎ of claim 1, wherein.

The present invention according to claim 4 (see, for example, FIGS. 1 to 7), the input shaft (2), the toroidal continuously variable transmission (10), the planetary gear mechanism (30), the low / high switching mechanism ( 20) and the output shaft (3) is arranged on one axis.
A continuously variable transmission (1 ₁ , 1 ₂ ) according to claim 2 or 3 , characterized in that

The present invention according to claim 5 (see, for example, FIG. 8) includes an input shaft (2) connected to a drive source and a rotation input to the input disk (11A, 11B) based on the rotation of the input shaft (2). To a continuously variable transmission (Vout) and output from the output disc (12A, 12B), a toroidal continuously variable transmission (10), a planetary gear mechanism (30), a low engagement element (L) and a high engagement A continuously variable transmission comprising a low / high switching mechanism (20) capable of switching between a low mode and a high mode depending on the engagement state with the coupling element (H), and an output shaft (3) connected to the drive wheel. In machine (1),
A first transmission shaft (71) for transmitting continuously variable speed rotation (Vout) of the output disk (12A, 12B) to the planetary gear mechanism (30);
A second transmission shaft (75, 175, 275) capable of transmitting continuously variable speed rotation (Vout) of the output disk (12A, 12B) to the output shaft (3) by bypassing the planetary gear mechanism (30);
A drive shaft (210) connected coaxially to the input shaft (2) and connected to a PTO device;
An input rotation output gear (201) fixed to the input shaft (2);
A reverse input gear (202) meshing with the input rotation output gear (201);
A rotating shaft (203) fixed to the reversing input gear (202) and disposed on an axis parallel to the input shaft (2) ,
In the low mode, the rotation of the input shaft (2) and the continuously variable speed rotation (Vout) of the first transmission shaft (71) are rotationally synthesized by the planetary gear mechanism (30) and the output shaft ( 3)
During the high mode, the continuously variable speed rotation (Vout) is transmitted to the output shaft (3) via the second transmission shaft (75, 175, 275).
The toroidal continuously variable transmission (10) and the planetary gear mechanism (30) are arranged on the rotating shaft (203),
The input disk (11A, 11B) receives rotation of the rotating shaft (203).
Lying in the continuously variable transmission (1 ₃₎ it characterized.

According to the sixth aspect of the present invention (see, for example, FIG. 8), the second transmission shaft has an input gear (273) fixed to one end and an output gear (276) fixed to the other end. The counter shaft (275) is rotatably arranged on the drive shaft (210).
A continuously variable output gear (which rotates at the continuously variable speed rotation (Vout) in conjunction with the output disk (12A, 12B) and meshes with the input gear (273) of the counter shaft (275) at least in the high mode. 272) and
An output shaft interlocking gear (278) interlocking with the output shaft (3) at least in the high mode;
The continuously variable transmission (1 ₃ ) according to claim 5, wherein:

According to a seventh aspect of the present invention, the input shaft (2), the drive shaft (210), and the counter shaft (275) are disposed on a first shaft (CT1),
The toroidal continuously variable transmission (10), the planetary gear mechanism (30), the low / high switching mechanism (20), and the output shaft (3) are parallel to the first shaft (CT1). Arranged on (CT2),
The continuously variable transmission (1 ₃ ) according to claim 6 , characterized in that:

According to the eighth aspect of the present invention (see, for example, FIGS. 3, 4, and 7), the high engagement element includes the second transmission shaft (75, 175) and the output disk (12A, 12B). High clutch (H) interposed between the
The continuously variable transmission (1) according to any one of claims 1 to 7, wherein the continuously variable transmission (1) is provided.

According to a ninth aspect of the present invention (see, for example, FIGS. 1, 3, 5, 6, 7, and 8), the low engagement element includes the planetary gear mechanism (30) and the output shaft (3). A low clutch (L) interposed between
The continuously variable transmission (1) according to any one of claims 1 to 8, wherein the continuously variable transmission (1) is provided.

According to the tenth aspect of the present invention (see, for example, FIGS. 1, 3, 5, 6, 7, and 8), the planetary gear mechanism (30) is connected to the first transmission shaft (71). A sun gear (S), a ring gear (R) connected to the output shaft (3) via the low clutch (L), a first pinion (P1) meshing with the sun gear (S), and the ring gear ( A second pinion (P2) meshing with R), and a carrier (C) connected to the input shaft (2) and a double pinion planetary gear (DP).
The continuously variable transmission (1) according to claim 9 , wherein the continuously variable transmission (1) is provided.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, the first transmission shaft that transmits the continuously variable rotation of the output disk to the planetary gear mechanism and the continuously variable rotation of the output disk that can be transmitted to the output shaft bypassing the planetary gear mechanism. 2 transmission shafts, and in the low mode, the rotation of the input shaft and the continuously variable speed rotation of the first transmission shaft are rotationally synthesized by the planetary gear mechanism and transmitted to the output shaft. In the high mode, the second transmission shaft is transmitted. Since the continuously variable speed rotation is transmitted to the output shaft via the transmission shaft, the continuously variable transmission in the axial direction can be made more compact than, for example, a uniaxial continuously variable transmission. However, it is possible to improve the durability and compactness of the second transmission shaft that does not transmit torque in the low mode and its rotation support member, and it is also possible to reduce the size of the continuously variable transmission in the radial direction. .

  Further, since the planetary gear mechanism is configured to transmit the continuously variable transmission of the toroidal-type continuously variable transmission only in the low mode, the number of teeth in each gear of the planetary gear mechanism is reduced, and especially the pinion diameter is reduced to a small diameter. The planetary gear mechanism can be made compact, and the continuously variable transmission in the radial direction can be made compact.

Furthermore , the toroidal continuously variable transmission is arranged on the input shaft, and the rotation of the input shaft is input to the input disk. Therefore, the input disk of the toroidal continuously variable transmission is rotated forward from the input shaft. Can be input, and the reverse rotation can be output from the output disk.

According to the present invention according to claim 2, since the second transmission shaft is a arranged a counter shaft on an axis parallel to the input shaft, a continuously variable rotation of the toroidal type continuously variable transmission by bypassing the planetary gear mechanism It can be possible to transmit to the output shaft. In addition, since the reversing gear is provided, the continuously variable speed rotation that is reversed with respect to the rotation of the input shaft in the toroidal continuously variable transmission is re-reversed and transmitted to the countershaft. , The output rotation can be transmitted to the output shaft by normal rotation.

According to the third aspect of the present invention, since the second transmission shaft is a counter shaft disposed on an axis parallel to the input shaft, the continuously variable speed rotation of the toroidal continuously variable transmission device is bypassed by the planetary gear mechanism. It can be possible to transmit to the output shaft. In addition, since the continuously variable transmission of the toroidal continuously variable transmission is transmitted to the countershaft by the belt-like member, the continuously variable transmission rotated by the toroidal continuously variable transmission with respect to the input shaft rotation is not reversed. That is, the output rotation can be transmitted to the output shaft by forward rotation.

According to the fourth aspect of the present invention, the input shaft, the toroidal continuously variable transmission, the planetary gear mechanism, the low / high switching mechanism, and the output shaft are arranged on one shaft. In addition, it can be suitably used for a vehicle in which a driving source is provided on one side in the front-rear direction and a wheel on the other side in the front-rear direction is a driving wheel.

According to the fifth aspect of the present invention, the toroidal continuously variable transmission is disposed on a rotating shaft disposed on an axis parallel to the input shaft, and the rotation of the rotating shaft is input to the input disk. Therefore, the reverse rotation based on the rotation of the input shaft can be input to the input disk of the toroidal continuously variable transmission, and the forward rotation can be output from the output disk.

According to the sixth aspect of the present invention, the second transmission shaft is a countershaft rotatably disposed on a drive shaft that is coaxial with the input shaft, and the toroidal continuously variable transmission and the planetary gear mechanism are provided on the input shaft. It is possible to transmit continuously variable speed rotation of the toroidal type continuously variable transmission to the output shaft by bypassing the planetary gear mechanism. it can. Further, in the toroidal continuously variable transmission, the continuously variable speed rotation that is normal rotation with respect to the rotation of the input shaft is reversed and transmitted to the countershaft. In other words, the output rotation can be transmitted to the output shaft by normal rotation.

According to the seventh aspect of the present invention, the input shaft, the drive shaft, and the counter shaft are disposed on the first shaft, and the toroidal continuously variable transmission, the planetary gear mechanism, the low / high switching mechanism, and the output shaft are: Since it arrange | positions on the 2nd axis | shaft parallel to a 1st axis | shaft, it can use suitably for the working vehicle which can connect a working machine etc. via PTO apparatuses, such as a tractor, for example.

According to the eighth aspect of the present invention, since the high engagement element is a high clutch interposed between the second transmission shaft and the output disk, the second transmission shaft rotates at a high speed in the low mode. It can be rotated by rotating the output shaft, which is a low rotation, without inputting continuously variable speed rotation, reducing oil agitation loss during low mode, and improving the durability of the rotation support member of the second transmission shaft. Can be planned.

According to the ninth aspect of the present invention, since the low engagement element is a low clutch interposed between the planetary gear mechanism and the output shaft, the rotation of the input shaft and the continuously variable rotation in the planetary gear mechanism in the low mode. Can be transmitted to the output shaft.

According to the tenth aspect of the present invention, the planetary gear mechanism is meshed with the sun gear connected to the first transmission shaft, the ring gear connected to the output shaft via the low clutch, and the first pinion and the ring gear meshed with the sun gear. Since the second pinion is supported by a double pinion planetary gear having a carrier connected to the input shaft, torque circulation can be made by combining the rotation of the input shaft and the continuously variable speed rotation. it can.

<First Embodiment>
A first embodiment according to the present invention will be described below with reference to FIGS. First, along the Figures 1 and 2, illustrating a continuously variable transmission 1 ₁ of the schematic structure according to a first embodiment of the present invention. Since the continuously variable transmission ₁₁ is particularly suitable for being mounted on an FR (front engine / rear drive) type vehicle or the like, in the following description, the left side in the figure is the “front side”, The right side is referred to as “rear side” (excluding FIG. 2).

As shown in FIG. 1, a continuously variable transmission (IVT) 11 according to the _first embodiment includes an input shaft 2, a toroidal continuously variable transmission (hereinafter referred to as “variator”) 10, A transmission shaft (hereinafter simply referred to as “sleeve shaft”) 71, a planetary gear mechanism 30, a low / high switching mechanism 20, and an output shaft 3 are provided coaxially with the input shaft 2 (output shaft 3). A second transmission shaft (hereinafter referred to as “counter shaft”) 75 is provided on an axis parallel to the input shaft 2.

  The variator 10 is of a full toroidal type, and includes an input disk 11A connected on the input shaft 2, an input disk 11B connected to the input shaft 2 via a carrier C of a planetary gear mechanism 30 described later, and a sleeve shaft 71. Two output disks 12A and 12B connected to each other, and power rollers 14A and 14B sandwiched between the two input disks 11A and 11B and the output disks 12A and 12B. The input disks 11A and 11B and the output disks 12A and 12B are arranged so as to be opposed to each other, constitute double cavities 13A and 13B with two rows of power rollers interposed therebetween, and cancel the thrust force between the disks. Become.

  A plurality of power rollers 14A, 14B are arranged at substantially equal positions in the circumferential direction of the annular double cavities 13A, 13B (for example, three in one cavity), and are composed of spherical bearings, levers, etc. (not shown). The link mechanism is pressed by hydraulic control. Further, as will be described in detail later, the clamping pressure at which the input disks 11A and 11B clamp the power rollers 14A and 14B is controlled by the hydraulic pressure, and the power rollers 14A and 14B are tilted autonomously. The contact radius between 11B and the output disks 12A and 12B is changed, and the speed is continuously changed. In the present variator 10, since the output disks 12A and 12B rotate reversely with respect to the input disks 11A and 11B, the speed ratio becomes-(minus). A sleeve shaft 71 is connected to the output disks 12A and 12B on the inner peripheral side, and a counter gear (stepless rotation output gear) 72 is disposed so as to be interlocked with the output disks 12A and 12B. ing.

  The planetary gear mechanism 30 includes a double pinion planetary gear (hereinafter simply referred to as “planetary gear”) DP, a carrier C having two pinions P1 and P2 (first pinion and second pinion), and a sun gear S meshing with the pinion P1. And a ring gear R meshing with the pinion P2. The sun gear S is connected to the sleeve shaft 71 connected to the output disks 12A and 12B, and the carrier C is connected to the input shaft 2 and to the input disk 11B. The ring gear R is connected to a low clutch (low engagement element) L of the low / high switching mechanism 20, and is connected to the output shaft 3 by the engagement of the low clutch L.

  On the other hand, the counter shaft 75 has an input gear 73 fixed to the front end and meshed with the counter gear 72, and an output gear 76 fixed to the rear end. . Between the output gear 76 of the counter shaft 75 and the output shaft interlocking gear 78, a reversing gear 77 meshing with both the gears 76, 78 is disposed. The output shaft interlocking gear 78 is switched between low and high. A high clutch (high engagement element) H of the mechanism 20 is connected. The output shaft interlocking gear 78 is connected to the output shaft 3 when the high clutch H is engaged.

In the skeleton diagram of the continuously variable transmission shown in FIG. 1, the high clutch H is disposed so as to be interposed between the output shaft interlocking gear 78 and the output shaft 3. in the continuously variable transmission 1 ₁ according to the present invention which will be described later, output disk 12A, are arranged so as to be interposed between 12B and the counter gear 72.

Next, it will be described with reference to FIGS. 1 and 2 the operation of the continuously variable transmission 1 _1.

For example, in or backward when at the start of the vehicle installed with a continuously variable transmission 1 _1, with low-high switching mechanism 20 based on hydraulic control by the shift lever or a hydraulic control device (not shown) is controlled, the high clutch H is released At the same time, the low clutch L is engaged, and the continuously variable transmission ₁₁ is set to the low mode. Then, as shown in FIG. 1, the rotation of the input shaft 2 connected to the engine output shaft is transmitted to the input disks 11A and 11B of the variator 10 and the carrier C of the planetary gear DP. Of these, the rotation of the input shaft 2 input to the input disks 11A and 11B is shifted by the variator 10, and the variator output rotation Vout is output from the output disks 12A and 12B and input to the sun gear S.

  When the variator output rotation Vout is input to the sun gear S, the rotation of the input shaft 2 (rotation of the carrier C) and the variator output rotation Vout (rotation of the sun gear S) are torque-circulated in the planetary gear DP as shown in FIG. And output from the ring gear R. The output rotation of the ring gear R is an output rotation that is shifted to a width from the reverse rotation of the deceleration to the normal rotation of the deceleration via the neutral position (GN point) according to the width of the gear ratio of the variator 10. The output rotation of the ring gear R is output to the output shaft 3 via the low clutch L as the output rotation OutL in the low mode state, as shown in FIG.

  In the low mode that forms the transmission path as described above, when the variator output rotation Vout (gear ratio of the variator 10) is in the gear neutral state GN indicated by the chain line in FIG. In the neutral state, that is, the output rotation OutL in the low mode is in the neutral state. In this state, the engine speed (the rotation of the input shaft 2) and the rotation of the output shaft 3 are irrelevant. Therefore, for example, when switching to the travel range, the gear ratio of the variator 10 is adjusted to the gear neutral state GN and then the low speed. By engaging the clutch L, it is not necessary to absorb the rotational speed difference, and there is no need to provide a device that absorbs the rotational speed difference, such as a torque converter.

  Here, for example, if a shift lever (not shown) is in the reverse (R) range, and the gear ratio of the variator 10 is increased according to the vehicle speed or the accelerator opening, for example, from this gear neutral state GN (in FIG. 2). When the variator output rotation Vout is shifted downward), the output rotation OutL of the output shaft 3 increases to the reverse rotation side and increases to the reverse side.

  On the other hand, for example, if a shift lever (not shown) is in the drive (D) range and the gear ratio of the variator 10 is made smaller than the gear neutral state GN, for example, according to the vehicle speed and the accelerator opening (in FIG. When the variator output rotation Vout is shifted upward), the output rotation OutL of the output shaft 3 increases to the forward rotation side and increases to the forward side.

Subsequently, in the low mode state, the output rotation OutL of the output shaft 3 is increased (the transmission ratio of the variator 10 is reduced), and reaches the transmission ratio at the upper end in FIG. When the shift is determined according to the opening, the low / high switching mechanism 20 is controlled based on hydraulic control by a hydraulic control device (not shown), the low clutch L is released, and the high clutch H is engaged. The continuously variable transmission ₁₁ is put into a high mode state.

  Then, as shown in FIG. 1, the variator output rotation Vout is reversely input to the counter shaft 75 via the counter gear 72 and the input gear 73, and the rotation of the counter shaft 75 is linked to the output gear 76, the reverse gear 77 and the output shaft. It is output to the output shaft 3 via the gear 78 (reversed and re-reversed).

  In the switching (sink change) between the low mode state and the high mode state described above, the gear ratios of the respective gears are set so that the switching is performed at the same speed ratio at which the speed ratio of the variator 10 (variator output rotation Vout) is minimized. Is set. In other words, in the low mode state, the output rotation OutL is increased as the gear ratio of the variator 10 is decreased, and in the high mode state, on the contrary, the gear ratio of the variator 10 is shifted to a larger speed at the sync change. As it goes on, the output rotation OutH is increased.

  In the low mode described above, when the high clutch H is disposed between the output shaft 3 and the output shaft interlocking gear 78 as in the continuously variable transmission shown in FIG. 1, the counter shaft 75 or the like is the variator. When the high clutch H is disposed between the output disks 12A and 12B and the counter gear 72 as in the continuously variable transmission shown in FIG. 3 to be described later, the counter shaft or the like is output. Based on the rotation of the shaft 3 (low mode output rotation OutL), the wheel rotates idly.

  In the high mode, since the variator output rotation Vout is input to the sun gear S and the rotation of the input shaft 2 is input to the carrier C, the ring gear R rotates idly at the low mode output rotation OutL.

Next will be described a first detailed configuration of the continuously variable transmission 1 ₁ according to the embodiment of the present invention along 3-5. 3 is an overall sectional view of the continuously variable transmission, FIG. 4 is an enlarged sectional view showing a front portion of the continuously variable transmission, and FIG. 5 is an enlarged sectional view showing a rear portion of the continuously variable transmission.

CVT (IVT) 1 ₁ is housed in a transmission case 7, the case 7, the main casing 5 cylindrical, housing case 4 and the main casing 5 is fixed to the front side of the main case 5 It consists of an end case 6 fixed to the rear side. The housing case 4 has a front end coupled to the engine, and houses a damper device (not shown). That is, the present IVT1 _1, since having a gear neutral (GN) as described above, was required in a conventional automatic transmission (AT) and a continuously variable transmission (CVT), the starting device such as a torque converter required Therefore, only a damper device that absorbs vibration and pulsation of the engine is sufficient in the housing case 4.

  The main case 5 is provided with a toroidal continuously variable transmission (variator) 10, a high clutch H of a low / high switching mechanism 20, and a planetary gear mechanism 30, and the end case 6 has a low / high switching mechanism. 20 low clutches L are arranged, and the rear end surface of the main case 5 and the front end surface of the end case 6 are connected and fixed to form an integral storage portion. A lower portion of the main case 5 is opened, and the opening is closed by an oil pan 94 that houses the hydraulic control device 90. The oil pump 93, the valve body 91, and the fulcrum block 92 are accommodated in the oil pan 94, and are fixed to the opening of the main case 5.

  A front partition plate 8 is fixed so as to be sandwiched between the housing case 4 and the main case 5, and as shown in detail in FIG. 4, a central boss portion 8a of the partition plate 8 is interposed via a needle bearing b1. A front portion of the input shaft (main shaft) 2 is rotatably supported. The front end 2a (front end) of the input shaft 2 extends into the housing case interior 4a and is connected to the engine output shaft via a damper device in the housing case interior 4a.

  A cylindrical support plate 41 is integrally fixed to the input shaft 2 so as to include the boss portion 8a. The reverse side of the variator 10 is provided between the front side of the support plate 41 and the front partition plate 8. A one-way clutch F for preventing input (preventing loosening) is provided. A drum member 42 is fixed to the outer peripheral side of the support plate 41, and an input disk 11A is supported between the inner peripheral surface of the drum member 42 and the outer peripheral surface of the input shaft 2, The outer peripheral side rear portion of the input disk 11A and the rear tip portion of the drum member 42 are spline-engaged. A cylinder is formed by the support plate 41 and the drum member 42 on the back surface (front side) of the input disk 11 </ b> A, and includes a hydraulic actuator 40 that generates a clamping force of the variator 10.

  The hydraulic actuator 40 is provided with pistons 43 and 44 with a leaf spring 45 interposed therebetween, an oil chamber 46 between the piston 43 and the cylinder, and an oil chamber between the piston 44 and the input disk 11A. 47 has a double piston structure. From the valve body 91 to the oil chambers 46 and 47, oil passages a1 and a2 in the main case 5, oil passages a3 and a4 in the front partition plate 8, and oil passages a5 and a6 in the support plate 41 are provided. Thus, the hydraulic pressure is supplied, thereby pressing the input disk 11A backward with respect to the input shaft 2.

  On the other hand, the sleeve shaft 71 is rotatably supported via needle bearings b2 and b10 (see FIG. 5) from approximately the middle to the rear of the input shaft 2 on the outer peripheral side. The output disks 12A and 12B are arranged in spline engagement, the input disk 11B is rotatably fitted to the rear outer peripheral portion, and the sun gear S is formed at the rear end (see FIG. 3, see FIG.

  The output disk 12B has a disk part 12Ba on the rear side and a sleeve part 12Bb that covers the sleeve shaft 71 on the inner peripheral side, and the front end of the sleeve part 12Bb is the back surface (rear side) of the output disk 12A. The pressure of the hydraulic actuator 40 is transmitted to the disk part 12Ba via the input disk 11A, the power roller 14A, the output disk 12A, and the sleeve part 12Bb. The pressing force transmitted to the disk portion 12Ba is received by the rear portion of the input shaft 2 via the power roller 14B, the input disk 11B, the carrier C described later, and the retaining member 102, that is, the clamping force of the variator 10. Is a closed loop system via the input shaft 2.

  A plurality of (three) power rollers 14A are sandwiched between an annular arc surface 11a formed on the front input disk 11A and an annular arc surface 12a formed on the output disk 12A, respectively. A plurality (three) of power rollers 14B are sandwiched between an annular arc surface 11a formed on the rear input disk 11B and an annular arc surface 12a formed on the output disk 12B. Two circular cavities 13A and 13B having a circular cross section are formed by the arc surfaces 11a and 12a facing each other, and the centers of the power rollers 14A and 14B are located at the centers of the circular cavities 13A and 13B. It rotates around the center axis that passes through. That is, the variator 10 is made of a full toroidal double cavity type, and therefore has a double cavity (2 rows), so that the torque capacity is doubled as compared with the one row, and the input disks and output disks are The thrust force cancels each other, the bearing load does not occur, and the two contact points of the power rollers 14A and 14B are on opposite sides of the center point of the cavities 13A and 13B. Thrust force does not work.

  A link mechanism (not shown) is connected to each of the three power rollers 14A and 14B located in the cavities 13A and 13B, and hydraulic actuators drive the power rollers 14A and 14B through the link mechanisms. (Not shown) is provided in the volkram block 92 (not shown because the rear side volkram block is arranged offset from the counter shaft 75). That is, the control block of the volkrum block 92 is formed with the same number of hydraulic actuators as the number of power rollers 14A and 14B and hydraulic circuits communicating with the actuators. The predetermined hydraulic pressure is applied.

  The hydraulic actuator 40 applies a pressing force that the power rollers 14A, 14B press against the circular arc surfaces 11a, 12a of the input disks 11A, 11B and the output disks 12A, 12B with a predetermined pressure. A traction force acts between each power roller and each disk based on the presence of oil. That is, power is transmitted to the variator 10 between the input disks 11A and 11B and the output disks 12A and 12B by the traction drive. The power rollers 14A and 14B are controlled in inclination by the link mechanism and the hydraulic actuator (reaction force), and the traction force (hydraulic actuator 40) acting on the contact surface between the power roller and the disk and the reaction force. Based on the relationship, the inclination of the power rollers 14A and 14B is autonomously controlled to control the shift.

  Further, the full toroidal variator 10 is capable of shifting with little force by shifting the power rollers 14A and 14B in the direction orthogonal to the axis without thrust force acting on the power rollers 14A and 14B, but in the opposite direction. When it rotates, the clamping force of the power rollers 14A and 14B is loosened. For this reason, even if reverse rotation acts on the variator 10 due to reverse rotation of the engine, the one-way clutch F prevents the variator 10 from rotating reversely.

  On the other hand, a support plate 101 fixed to the main case 5 is fitted on the outer peripheral side front portion of the sleeve portion 12Bb between the output disks 12A and 12B via thrust bearings b7 and b9 and a needle bearing b8. In addition, a counter gear 72 is rotatably disposed on the outer peripheral portion of the boss portion 101a of the support plate 101 via ball bearings b3 and b4. In addition, a high clutch H of the low / high switching mechanism 20 is disposed on the outer peripheral side rear portion of the sleeve portion 12Bb using the back surface (front side) of the disk portion 12Ba.

  The high clutch H includes a friction plate 51 including an outer friction plate 51a and an inner friction plate 51b, and a hydraulic servo 50 that allows the friction plate 51 to be freely engaged and disengaged. A drum member 52 is fixed in a non-rotatable manner on the outer peripheral side of the disk portion 12Ba of the output disk 12B, and the outer friction plate 51a is spline-engaged with the inner peripheral side of the drum member 52. The inner friction plate 51 b is spline-engaged with a hub member 58 connected to the counter gear 72.

  The hydraulic servo 50 includes a piston member 53 that is slidable in the axial direction with respect to the sleeve portion 12Bb in a form in which the back surface of the disk portion 12Ba is a cylinder, and is engaged with the sleeve portion 12Bb with respect to the front side in the axial direction. It has a stopped cancel plate 54 and a return spring 55 that is contracted between the piston member 53 and the cancel plate 54, thereby forming a hydraulic oil chamber 56 and a cancel oil chamber 57. ing.

  The working oil chamber 56 is supplied with working oil (in the high mode) via oil passages a11 and a12 in the support plate 101 connected to the valve body 91 and oil passages a13 and a14 in the sleeve portion 12Bb. . When hydraulic pressure is supplied to the hydraulic oil chamber 56, the outer peripheral end of the piston member 53 presses the friction plate 51 and the high clutch H is engaged, whereby the output disks 12A and 12B and the counter gear 72 are integrated. Rotate. The cancellation oil chamber 57 is supplied with lubricating oil from a lubricating oil passage (not shown), is made oiltight by the supply of lubricating oil, and cancels the centrifugal hydraulic pressure when the high clutch H is released.

  A shaft hole 101b is formed on the lower side of the support plate 101, and a front end portion of the counter shaft 75 is rotatably supported via a thrust bearing b5. An input gear 73 that meshes with the counter gear 72 is non-rotatably splined to the front portion of the counter shaft 75, that is, when the high clutch H is engaged (in the high mode). The rotation of the output disks 12A and 12B (hereinafter referred to as “variator output rotation Vout”) is transmitted to the counter shaft 75.

  On the other hand, as shown in FIG. 5, the planetary gear DP of the planetary gear mechanism 30 is disposed on the rear outer peripheral side of the input shaft 2. The carrier C of the planetary gear DP is configured such that the front carrier plate Cf on the front side and the rear carrier plate Cr on the rear side are connected to each other while supporting the pinion shafts Cp1 and Cp2, and the inner peripheral side of the rear carrier plate Cr is The front portion is supported by the input shaft 2 and the front portion thereof is spline-engaged so that the entire carrier C rotates integrally with the rotation of the input shaft 2. On the rear surface of the rear carrier plate Cr, a retaining member (for example, a nut screwed to the input shaft 2) 102 is disposed, and the entire carrier C is locked so as not to move backward with respect to the input shaft 2. Has been.

  A dock m is formed at the front end of the front carrier plate, and a dock n is also formed on the back surface of the input disk 11B. When the docks m and n are engaged, the input disk 11B, the carrier C, Are connected together in the direction of rotation. On the outer peripheral side of both docks m and n, a sprocket 103 is integrally disposed to fit between the input disk 11B and the front carrier plate Cf of the carrier C. The sprocket 103 is not shown. This is connected to the drive shaft of the oil pump 93 through the chain. That is, when engine rotation is input to the input shaft 2, the sprocket 103 is rotated via the carrier C, and the oil pump 93 is driven in an interlocking manner.

  A first pinion P1 and a second pinion P2 are rotatably supported on the pinion shafts Cp1 and Cp2. A sun gear S formed on the outer peripheral side of the rear end of the sleeve shaft 71 is meshed with the first pinion P1, and a ring gear R is meshed with the second pinion P2. The ring gear R is supported by the flange-like member 81 on the rear end side and is engaged with the spline. The planetary gear DP is lubricated from the inner peripheral side of the sun gear S through oil passages a31 and a32 formed in an output shaft 3 (described later) and oil passages a33 and a34 in the input shaft 2 from an oil passage (not shown). Oil is supplied.

  The flange-shaped member 81 is rotatably supported on the outer peripheral surface of the rear end of the input shaft 2 via a needle bearing b14, and a hub member 82 connected to the low clutch L is splined on the outer peripheral side of the inner peripheral portion. It is engaged and locked so that it cannot move in the axial direction. Further, a flange-like member 83 is rotatably supported on the outer peripheral side of the hub member 82 via a thrust bearing b13. On the further outer peripheral side of the flange-like member 83, the flange-like member 83 is connected to the spline. The combined output shaft interlocking gear 78 is rotatably supported through a thrust bearing b11 and a needle bearing b12. The output shaft interlocking gear 78 is connected to the output shaft 3 via the flange-shaped member 83, a drum member 62 (described later), a parking gear 85, and a sleeve member 86. That is, each output shaft interlocking gear 78 includes the output shaft interlocking gear 78. The member is interlocked with the output shaft 3.

  A support plate 102 fixed to the main case 5 by bolts 111, 112, 113, etc. is disposed on the outer peripheral side of the inner peripheral portion of the output shaft interlocking gear 78. The output shaft interlocking gear 78 is rotatably supported by the boss portion 102a via bearings b17 and b18. A shaft hole 102b is formed on the lower side of the support plate 102, and the rear end of the counter shaft 75 is rotatably supported via a bearing b19. An output gear 76 is formed at the rear portion of the counter shaft 75, and a reversing gear 77 (see FIG. 1) is engaged. The reversing gear 77 is rotatably arranged in a shape parallel to the counter shaft 75 and the input shaft 2, that is, the axis center of the input shaft 2, the axis center of the reversing gear 77, and the axis center of the counter shaft 75 are The position is in the shape of a letter when viewed in the axial direction. The reversing gear 77 meshes with the output shaft interlocking gear 78, that is, the reversing gear 77, the output gear 76, the counter shaft 75, the input gear 73, and the counter gear 72 (see FIGS. 3 and 4) It is linked to the output shaft 3.

  On the other hand, the front end of the end case 6 is rotatably fitted to the rear end of the input shaft 2 and is rotatably supported by the end case 6 via a ball bearing b21. A more protruding output shaft 3 is provided. A flange member 3a is spline-engaged with the protruding portion of the output shaft 3 and is prevented from coming off by a nut 3b, and is connected to a drive shaft (not shown). The output shaft 3 is connected to drive wheels via a drive shaft, a differential device, and the like.

  On the outer peripheral side of the output shaft 3, a boss member 87 fixed by bolts 114, 115 and the like is disposed at the inner peripheral portion of the end case 6, and the output shaft 3 is interposed via a needle bearing b15 and a thrust bearing b16. The boss member 87 is also rotatably supported. A low clutch L of the low / high switching mechanism 20 is disposed on the outer peripheral side of the boss member 87.

  A sleeve member 86 whose front end portion inner peripheral side is fixed to the output shaft 3 is rotatably supported on the outer peripheral side of the boss member 87, and a parking gear 85 is provided on the outer peripheral side of the rear end portion of the sleeve member 86. It is fixed. Further, a drum member 62 is fixed to the front end portion of the parking gear 85, and the drum member 62, the parking gear 85, and the sleeve member 86 constitute a clutch drum that forms a cylinder of the hydraulic servo 60 of the low clutch L. is doing.

  In addition, a tooth surface 85a is formed on the outer peripheral surface of the parking gear 85, and a parking rod (not shown) can be engaged based on the driving of the parking gear mechanism to form a parking state. Yes. In addition, a resolver 89 of an output shaft rotation sensor for detecting the output shaft rotation speed is disposed on the rear side of the tooth surface 85a of the parking gear 85.

  The low clutch L includes a friction plate 61 including an outer friction plate 61a and an inner friction plate 61b, and a hydraulic servo 60 that allows the friction plate 61 to be freely engaged and disengaged. The outer friction plate 61a is spline-engaged on the inner peripheral side of the drum member 62, and the inner friction plate 61b is spline-engaged with a hub member 82 connected to the ring gear R. Further, a flange-like member 83 connected to the output shaft interlocking gear 78 is spline-engaged with the front end portion on the inner peripheral side of the drum member 62 and is locked to the front side in the axial direction.

  The hydraulic servo 60 includes a piston member 63 that is slidable in the axial direction with respect to the sleeve member 86 in a form in which the side surface of the parking gear 85 is a cylinder, and the sleeve member 86 is engaged with the front side in the axial direction. A cancel plate 64 that is stopped, and a return spring 65 that is contracted between the piston member 63 and the cancel plate 64 are provided, thereby forming a hydraulic oil chamber 66 and a cancel oil chamber 67. ing.

  The hydraulic oil is supplied to the hydraulic oil chamber 66 through the oil passages a21, a22, a23 in the boss portion 87 connected to the valve body 91 and the oil passage a24 in the sleeve member 86 (in the low mode). . When hydraulic pressure is supplied to the hydraulic oil chamber 66, the outer peripheral side end of the piston member 63 presses the friction plate 61 and the low clutch L is engaged, whereby the ring gear R of the planetary gear DP and the output shaft 3 are connected. Rotates together. The cancellation oil chamber 67 is supplied with lubricating oil from a lubricating oil passage (not shown), is made oiltight by the supply of lubricating oil, and cancels the centrifugal hydraulic pressure when the low clutch L is released.

Above the As explained by the continuously variable transmission 1 ₁ according to a first embodiment of the present invention, a sleeve shaft 71 for transmitting output disks 12A, the variator output rotation Vout of 12B to the planetary gear mechanism 30, the output disc 12A , 12B of the variator output rotation Vout is bypassed by the planetary gear mechanism 30 and can be transmitted to the output shaft 3, and in the low mode, the rotation of the input shaft 2 and the variator output rotation Vout of the sleeve shaft 71 Is rotated and synthesized by the planetary gear mechanism 30 and transmitted to the output shaft 3, and in the high mode, the variator output rotation Vout is transmitted to the output shaft 3 via the counter shaft 75. also it can be made compact in the continuously variable transmission 1 ₁ in the axial direction than the variable transmission However, the durability and compactness of the counter shaft 75 that does not transmit torque in the low mode and its rotation support members (bearings b3, b4, b5, b19, b17, b18, support plates 101, 102, etc.) can be achieved, it is possible to achieve even compaction of the continuously variable transmission 1 ₁ in a radial direction.

Further, since the planetary gear mechanism 30 is configured to transmit the output rotation Vout of the variator 10 only when in the low mode, the restriction on the number of teeth in each gear (S, P1, P2, R) of the planetary gear mechanism 30 is reduced. , in particular the diameter of the first pinion P1, P2 and can be smaller in diameter, can be made compact planetary gear mechanism 30, it is possible to continuously variable transmission 1 ₁ of the compact in the radial direction.

  Further, since the variator 10 is disposed on the input shaft 2 and the rotation of the input shaft 2 is input to the input disks 11A and 11B, the forward rotation from the input shaft 2 is applied to the input disks 11A and 11B of the variator 10. Rotation can be input, and reverse rotation can be output from the output disks 12A and 12B.

  Further, since the counter shaft 75 is arranged on an axis parallel to the input shaft 2, it is possible to transmit the output rotation Vout of the variator 10 to the output shaft 3 bypassing the planetary gear mechanism 30. Further, since the reversing gear 77 is provided, the variator output rotation Vout reversed with respect to the rotation of the input shaft 2 by the variator 10 is re-inverted and transmitted to the counter shaft 75. The rotation of 75 can be reversed again, that is, the output rotation can be transmitted to the output shaft 3 by normal rotation.

  In addition, since the input shaft 2, the variator 10, the planetary gear mechanism 30, the low / high switching mechanism 20, and the output shaft 3 are arranged on one axis, they are driven in one side in the front-rear direction, for example, an FR type automobile. There is a power source, and it can be suitably used for a vehicle (including a four-wheel drive vehicle) in which a wheel on the other side in the front-rear direction is a drive wheel.

  Furthermore, since the high clutch H interposed between the countershaft 75 and the output disks 12A and 12B is provided, the countershaft 75 does not input the variator output rotation Vout that is high in the low mode and is low. It can be rotated by the rotation of the output shaft 3 (ie, the output rotation Lout in the low mode) (see FIG. 2), the oil agitation loss is reduced in the low mode, and the rotation support member (bearing) of the counter shaft 75 (b3, b4, b5, b19, b17, b18, support plates 101, 102, etc.) can be improved in durability.

  In addition, since the low clutch L interposed between the planetary gear mechanism 30 and the output shaft 3 is provided, the combined rotation of the rotation of the input shaft 2 and the variator output rotation Vout in the planetary gear mechanism 30 in the low mode is performed on the output shaft. 3 can be transmitted.

  Further, the planetary gear mechanism 30 meshes with the sun gear S connected to the sleeve shaft 71, the ring gear R connected to the output shaft 3 via the low clutch L, the first pinion P1 and the ring gear R meshed with the sun gear S. Since it consists of a double pinion planetary gear DP that supports the second pinion P2 and has a carrier C connected to the input shaft 2, it is possible to circulate torque by synthesizing and outputting the rotation of the input shaft 2 and the variator output rotation Vout. It can be.

<Second Embodiment>
Next, a second embodiment obtained by partially changing the first embodiment will be described with reference to FIGS. In the second embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

CVT 1 ₂ according to the second embodiment, especially FR is suitably mounted (front-engine, rear drive) type vehicle such as CVT according to the first embodiment compared to machine _{1 1,} as shown in FIGS. 6 and 7, the output disks 12A, the transmission path between 12B and the counter shaft 75 rather than gears, constituted by transmission belt 173 and pulley 172, 174, also, It is configured without the reverse gear 77 (see FIG. 1).

  Specifically, as shown in FIG. 7, a counter pulley (stepless rotation output member) 172 is disposed on the transmission path output side of the high clutch H instead of the counter gear 72, and one counter shaft ( Instead of the input gear 73, an input pulley (input member) 174 is disposed on the front side (transmission path input side) of the second transmission shaft) 175. A transmission belt (belt-like member) 173 is wound around the counter pulley 172 and the input pulley 174. An output gear 176 that directly meshes with the output shaft interlocking gear 178 is disposed on the rear side (transmission path output side) of the counter shaft 175.

  That is, in the high mode in which the high clutch H is engaged, the output rotation Vout from the output disks 12A and 12B of the variator 10 is input to the counter shaft 175 via the counter pulley 172, the transmission belt 173, and the input pulley 174. At this time, the variator output rotation Vout (reverse rotation with respect to the rotation of the input shaft 2) is directly transmitted to the counter shaft 175 in the same rotation direction. Further, the rotation of the counter shaft 175 is inverted and transmitted to the output shaft interlocking gear 178 via the output gear 176, that is, the variator output rotation Vout as the normal rotation is output to the output shaft 3.

  In the low mode with the low clutch L engaged, as in the first embodiment, the rotation of the output shaft 3 causes the output shaft interlocking gear 178, the counter shaft 175, the transmission belt 173, the counter pulley 172, etc. Of course, the rotation of the countershaft 175 at this time is the reverse of that of the first embodiment.

Thus, in the continuously variable transmission 1 _2, yet one which can make it possible to transmit the output rotation Vout of the variator 10 to bypass the planetary gear mechanism 30 to the output shaft 3, transmits the variator output rotation Vout Since it is transmitted to the counter shaft 175 by the belt 173, the variator output rotation Vout reversed with respect to the rotation of the input shaft 2 by the variator 10 can be transmitted to the counter shaft 175 without being reversed, and the output shaft interlocking gear 178 Since the output is reversed, that is, the output rotation can be transmitted to the output shaft 3 by normal rotation.

Incidentally, the continuously variable transmission 1 ₂ according to the second embodiment, more than the described partial structure and operation and effect of is the same as the continuously variable transmission 1 ₁ according to the first embodiment, The description is omitted.

<Third Embodiment>
Next, a third embodiment obtained by partially changing the first embodiment will be described with reference to FIG. In the third embodiment, the same reference numerals are given to the same parts as those in the first embodiment, and the description thereof is omitted.

The continuously variable transmission 13 according to the _third embodiment is suitable for mounting on a work vehicle such as a tractor, for example, and is compared with the continuously variable transmission 11 according to the _first embodiment. The input shaft 2 and the output shaft 3 are not arranged coaxially (see FIG. 1), but as shown in FIG. 8, on the first axis CT1 coaxial with the input shaft 2, for example, A drive shaft 210 and a counter shaft 275 connected to a PTO (Power Take Off) device (not shown) are arranged, and a rotary shaft 203, a variator 10, and a planetary gear are arranged on a different second axis CT2 parallel to the input shaft 2. The mechanism 30 and the low / high switching mechanism 20 are arranged.

Specifically, as shown in FIG. 8, the continuously variable transmission 1 ₃ is provided with a drive shaft 210 connected to the input shaft 2, the outer periphery of the drive shaft 210, which is formed on the sleeve-like counter A shaft 275 is rotatably arranged with respect to the drive shaft 210. For example, a PTO drive shaft of a PTO device (not shown) is connected to the rear end (right side in FIG. 8) of the drive shaft 210, and the PTO shaft from which rotation rotated by the PTO device protrudes from the rear portion of the vehicle. Is output. Note that a working machine such as a tillage rotary can be connected to the PTO shaft, and is transmitted from the PTO shaft to the working machine as a driving rotation.

  On the other hand, an input rotation output gear 201 is fixed to the input shaft 2, and the input rotation output gear 201 meshes with the reverse input gear 202. The reverse input gear 202 is fixed to a rotary shaft 203 on the second axis CT2, and the rotation of the input shaft 2 is reversed by the input rotary output gear 201 and the reverse input gear 202 on the rotary shaft 203. Entered. A planetary gear DP of the variator 10 and the planetary gear mechanism 30 is disposed on the rotating shaft 203. The rotating shaft 203 is connected to the input disk 11A of the variator 10, the carrier C of the planetary gear DP, and the carrier C. It is connected to the input disk 11B.

  As in the first embodiment, a sleeve shaft 71 connected to the sun gear S is connected to the inner peripheral side of the output disks 12A and 12B of the variator 10, and the ring gear R is connected to the low gear. -It is connected to the low clutch L of the high switching mechanism 20. The ring gear R is connected to the output shaft 3 by the engagement of the low clutch L.

On the output disks 12A and 12B of the variator 10, a counter gear (stepless rotation output gear) 272 is arranged so as to be able to interlock with the output disks 12A and 12B, as in the first embodiment. Yes. Similarly, the counter shaft 275 is provided with an input gear 273 fixed to the front end and meshing with the counter gear 272, and an output gear 276 fixed to the rear end. Has been. Then, in the continuously variable transmission 1 ₃ according to the present embodiment, the output gear 276 is meshed directly with the output shaft engaging gear 278, the output shaft engaging gear 278, high low-high switching mechanism 20 It is connected to the clutch H. The output shaft interlocking gear 278 is connected to the output shaft 3 when the high clutch H is engaged.

  In the skeleton diagram of the continuously variable transmission shown in FIG. 8, the high clutch H is disposed so as to be interposed between the output shaft interlocking gear 278 and the output shaft 3. Similarly to the first embodiment, it may be disposed so as to be interposed between the output disks 12A and 12B and the counter gear 272.

Next, it will be described with reference to FIG. 8, operation of the continuously variable transmission 1 _3.

In the continuously variable transmission 13 according to the _third embodiment, the rotation of the input shaft 2 connected to the engine output shaft is transmitted to the input rotation output gear 201 and the drive shaft 210. The rotation of the input shaft 2 input to the drive shaft 210 is input to a PTO drive shaft (not shown), and is shifted by a PTO device based on an operation of a PTO shift lever (not shown), for example, and output to the PTO shaft. . On the other hand, the rotation of the input shaft 2 input to the input rotation output gear 201 is reversed (decelerated or increased by the gear ratio) by the reverse input gear 202 and input to the rotary shaft 203. The reverse rotation of the rotary shaft 203 is transmitted to the input disks 11A and 11B of the variator 10 and the carrier C of the planetary gear DP.

  Here, for example, in the low mode state in which the high clutch H is released and the low clutch L is engaged, the reverse rotation input to the input disks 11A and 11B is further reversed by the variator 10 and shifted. The variator output rotation Vout output from the output disks 12A and 12B via the sleeve shaft 71 is input to the sun gear S.

  When the variator output rotation Vout is input to the sun gear S, the reverse rotation (rotation of the carrier C) of the rotating shaft 203 and the variator output rotation Vout (rotation of the sun gear S) are combined by torque circulation in the planetary gear DP, and the ring gear. Output from R. As in the first embodiment, the output rotation of the ring gear R is from the reverse rotation of the deceleration to the normal rotation of the deceleration via the neutral position (GN point) according to the speed ratio width of the variator 10. The output rotation is shifted to a width, and the output rotation direction at this time is the opposite rotation direction to that of the first embodiment (see FIG. 2). The output rotation of the ring gear R is output to the output shaft 3 via the low clutch L as the output rotation OutL in the low mode state.

In the present continuously variable transmission 1 _3, when a gear neutral condition GN similarly engine speed (the rotation of the input shaft 2) and the rotation and the output shaft 3 is irrelevant, the drive during this shaft 210 Since the rotation of the engine is input to, the drive rotation can be output to the PTO shaft depending on the speed change state of the PTO device.

  On the other hand, for example, in the high mode state in which the low clutch L is released and the high clutch H is engaged, the reverse rotation input to the input disks 11A and 11B is reversed and shifted by the variator 10, and the output disk is changed. The variator output rotation Vout output from 12A and 12B via the counter gear 272 and the input gear 273 is reversely input to the counter shaft 275. Then, the rotation of the counter shaft 275 is reversed again via the output gear 276 and the output shaft interlocking gear 278 and is output to the output shaft 3 as normal rotation.

  As in the first embodiment, when the high clutch H is disposed between the output shaft 3 and the output shaft interlocking gear 278 in the low mode, the counter shaft 275 and the like are set to the variator output rotation Vout. When the high clutch H is disposed between the output disks 12A and 12B and the counter gear 272, the counter shaft 275 and the like rotate idly based on the rotation of the output shaft 3 (low mode output rotation OutL). It will be.

According to the continuously variable transmission 1 ₃ according to a third embodiment of the present invention as described above, the variator 10 is disposed on a rotating shaft 203 arranged on parallel to the input shaft 3 axis CT2 Thus, since the rotation of the rotary shaft 203 is input to the input disks 11A and 11B, a reverse rotation based on the rotation of the input shaft 2 can be input to the input disks 11A and 11B of the variator 10, and the output disks 12A and 12B. Can output normal rotation.

  Further, a counter shaft is rotatably disposed on a drive shaft 210 that is coaxial with the input shaft 2 and on the same axis CT1, and the variator 10 and the planetary gear mechanism 30 are disposed on a rotational shaft 203 disposed on an axis CT2 parallel to the input shaft 2. Since it is disposed above, the output rotation Vout of the variator 10 can be transmitted to the output shaft 3 by bypassing the planetary gear mechanism 30. Further, the output rotation Vout which is normal rotation with respect to the rotation of the input shaft 2 is reversed by the variator 10 and transmitted to the counter shaft 275, but the rotation of the counter shaft 275 is reversed again to the output shaft interlocking gear 278. That is, the output rotation can be transmitted to the output shaft 3 by normal rotation.

  Further, the input shaft 2, the drive shaft 210, and the counter shaft 275 are disposed on the first axis CT1, and the variator 10, the planetary gear mechanism 30, the low / high switching mechanism 20, and the output shaft 3 are connected to the first axis CT1. Since it arrange | positions on the parallel 2nd axis | shaft CT2, it can be used suitably for the working vehicle which can connect a working machine etc. via PTO apparatus like a tractor, for example.

Incidentally, the continuously variable transmission 1 ₃ according to the third embodiment, the above except the described partial configuration, operation and effect of is the same as the continuously variable transmission 1 ₁ according to the first embodiment, The description is omitted.

  In the first to third embodiments described above, an example in which a full toroidal continuously variable transmission is used as a continuously variable transmission has been described as an example. However, of course, a half toroidal continuously variable transmission is used. You may use. Further, the variator has been described as a double cavity type in which two cavities are formed. However, the variator may be a single cavity or may constitute three or more cavities.

  In the first to third embodiments, the counter shaft is used as the second transmission shaft. However, the present invention is not limited to this. For example, the inner axis of the main case 5 is coaxial with the center of the input shaft 2. The first transmission shaft and the second transmission shaft may be arranged coaxially, such as using a drum-shaped member that rotates along the peripheral surface, that is, the output rotation of the variator 10 is controlled by the planetary gear mechanism. Any device can be used as long as it can be transmitted to the output shaft 3 while bypassing the above.

  Further, in the second embodiment, the counter shaft 175 and the output disks 12A and 12B are rotationally connected to each other using a belt and a pulley. However, a chain and a sprocket may be used.

1 is a skeleton diagram showing a continuously variable transmission according to a first embodiment. FIG. It is a speed diagram of the continuously variable transmission which concerns on 1st Embodiment. 1 is an overall cross-sectional view showing a continuously variable transmission according to a first embodiment. It is sectional drawing which shows the front part of the continuously variable transmission which concerns on 1st Embodiment. It is sectional drawing which shows the rear part of the continuously variable transmission which concerns on 1st Embodiment. It is a skeleton figure which shows the continuously variable transmission which concerns on 2nd Embodiment. It is sectional drawing which shows the continuously variable transmission which concerns on 2nd Embodiment. It is a skeleton figure which shows the continuously variable transmission which concerns on 3rd Embodiment.

Explanation of symbols

1 continuously variable transmission 2 input shaft 3 output shaft 10 toroidal continuously variable transmission (variator)
11A Input disk 11B Input disk 12A Output disk 12B Output disk 20 Low / High switching mechanism 30 Planetary gear mechanism 71 First transmission shaft (sleeve shaft)
72 Continuously rotating output gear (counter gear)
73 Input gear 75 Second transmission shaft, counter shaft 76 Output gear 77 Reverse gear 78 Output shaft interlocking gear 172 Stepless rotation output member (counter pulley)
173 Belt-shaped member (transmission belt)
174 Input member (input pulley)
175 Second transmission shaft, counter shaft 176 Output gear 178 Output shaft interlocking gear 201 Input rotation output gear 202 Reverse input gear 203 Rotation shaft 210 Drive shaft 272 Stepless rotation output gear 273 Input gear 275 Second transmission shaft, counter shaft 276 Output Gear 278 Output shaft interlocking gear L Low engagement element (low clutch)
H High engagement element (high clutch)
DP Double pinion planetary gear S Sun gear C Carrier P1 First pinion P2 Second pinion R Ring gear Vout Continuously variable speed rotation CT1 First axis CT2 Second axis

Claims (10)

An input shaft connected to a drive source, is disposed on the input shaft, a toroidal-type continuously variable outputs from the shift to the output disc rotation of the input disk to which the rotation of the input shaft is inputted to the continuously variable rotation A transmission, a planetary gear mechanism, a low / high switching mechanism capable of switching between a low mode and a high mode according to an engagement state of the low engagement element and the high engagement element, an output shaft connected to the drive wheel, In a continuously variable transmission equipped with
A first transmission shaft for transmitting continuously variable speed rotation of the output disk to the planetary gear mechanism;
A second transmission shaft capable of transmitting continuously variable speed rotation of the output disk to the output shaft by bypassing the planetary gear mechanism;
In the low mode, the rotation of the input shaft and the continuously variable rotation of the first transmission shaft are rotationally synthesized by the planetary gear mechanism and transmitted to the output shaft,
In the high mode, the continuously variable speed rotation is transmitted to the output shaft via the second transmission shaft.
A continuously variable transmission. The second transmission shaft comprises a counter shaft having an input gear fixed to one end and an output gear fixed to the other end and disposed on an axis parallel to the input shaft,
A continuously variable output gear that rotates at the continuously variable speed in conjunction with the output disk at least in the high mode and meshes with the input gear of the countershaft;
An output shaft interlocking gear that interlocks with the output shaft at least in the high mode;
A reversing gear meshing with the output gear of the countershaft and the output shaft interlocking gear,
The continuously variable transmission according to claim 1 . The second transmission shaft includes a counter shaft having an input member fixed to one end and an output gear fixed to the other end and disposed on an axis parallel to the input shaft,
A continuously variable output member capable of rotating at the continuously variable speed rotation in conjunction with the output disk;
A belt-like member wound around the stepless rotation output member and the input member of the countershaft;
An output shaft interlocking gear that meshes with the output gear of the countershaft and interlocks with the output shaft at least in the high mode.
The continuously variable transmission according to claim 1 . The input shaft, the toroidal continuously variable transmission, the planetary gear mechanism, the low / high switching mechanism, and the output shaft are arranged on one axis.
4. The continuously variable transmission according to claim 2, wherein the continuously variable transmission. An input shaft connected to a drive source, a toroidal continuously variable transmission that outputs the rotation input to the input disk based on the rotation of the input shaft to a continuously variable speed rotation and output from the output disk, a planetary gear mechanism; In a continuously variable transmission including a low / high switching mechanism capable of switching between a low mode and a high mode depending on an engagement state between a low engagement element and a high engagement element, and an output shaft connected to a drive wheel ,
A first transmission shaft for transmitting continuously variable speed rotation of the output disk to the planetary gear mechanism;
A second transmission shaft capable of transmitting continuously variable speed rotation of the output disk to the output shaft by bypassing the planetary gear mechanism;
A drive shaft connected coaxially to the input shaft and connected to a PTO device;
An input rotation output gear fixed to the input shaft;
A reverse input gear meshing with the input rotation output gear;
A rotating shaft fixed to the reversing input gear and disposed on an axis parallel to the input shaft ,
In the low mode, the rotation of the input shaft and the continuously variable speed rotation of the first transmission shaft are combined by the planetary gear mechanism and transmitted to the output shaft,
In the high mode, the continuously variable speed rotation is transmitted to the output shaft via the second transmission shaft,
The toroidal continuously variable transmission and the planetary gear mechanism are disposed on the rotating shaft,
The input disk is inputted with rotation of the rotary shaft.
Continuously variable transmission that be characterized in that. The second transmission shaft includes a counter shaft having an input gear fixed to one end and an output gear fixed to the other end, and rotatably disposed on the drive shaft.
A continuously variable output gear that rotates at the continuously variable speed in conjunction with the output disk at least in the high mode and meshes with the input gear of the countershaft;
An output shaft interlocking gear that interlocks with the output shaft at least in the high mode,
The continuously variable transmission according to claim 5 . The input shaft, the drive shaft, and the counter shaft are disposed on a first axis;
The toroidal continuously variable transmission, the planetary gear mechanism, the low / high switching mechanism, and the output shaft are disposed on a second axis parallel to the first axis.
The continuously variable transmission according to claim 6 . The high engagement element is a high clutch interposed between the second transmission shaft and the output disk.
A continuously variable transmission according to any one of claims 1 to 7 . The low engagement element is a low clutch interposed between the planetary gear mechanism and the output shaft.
A continuously variable transmission according to any one of claims 1 to 8 . The planetary gear mechanism includes a sun gear connected to the first transmission shaft, a ring gear connected to the output shaft via the low clutch, a first pinion meshing with the sun gear, and a second pinion meshing with the ring gear. And a carrier connected to the input shaft and having a double pinion planetary gear.
The continuously variable transmission according to claim 9 .

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