JP4127162B2 - Multi-speed transmission - Google Patents

Description

  The present invention relates to an improvement of a multi-stage transmission capable of shifting at least seven forward speeds.

  As an automatic transmission for a vehicle, one using a plurality of planetary gear devices, clutches and brakes is often used. As such an automatic transmission, there has been proposed a multi-speed transmission capable of multi-speed shifting of 7 or more forward speeds. The automatic transmission described in Patent Document 1 is an example thereof, and multi-stage shifting of 9 to 12 forward speeds is possible by using three or four sets of planetary gear devices.

JP 2002-206601 A JP-A-8-105496 JP 2000-199549 A JP 2000-266138 A JP 2001-82555 A JP 2002-227940 A JP 2002-295609 A Japanese Patent No. 2956173

  By the way, in such a multi-stage transmission, (a) the overall gear ratio range is sufficiently wide, (b) the steps of each gear ratio are arranged in an equal ratio or close to it, and (c) the engagement element ( The number of clutches and brakes is as small as possible, (d) it is easy to change their engagement elements when shifting, (e) the number of planetary gear units is as small as possible, and (f) a compact configuration. The gear ratio ρ (the number of teeth of the sun gear / the number of teeth of the ring gear) of the planetary gear device is preferably within a range of about 0.3 to 0.7, but it is difficult to satisfy all of these requirements, and it is not always satisfactory. It wasn't possible. For example, the multi-stage transmission described in Patent Document 1 needs to change up to four engagement elements when changing gear positions, which requires complicated and highly accurate shift control and may cause a shift shock. On the other hand, the planetary gear device has a problem that the gear ratio ρ is 0.273 to 0.778, and it is difficult to make it compact.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to meet demands for speed ratio characteristics such as speed ratio steps and overall speed ratio width, speed controllability, compactness, etc. at a high level. An object of the present invention is to provide a multi-stage transmission that can be satisfied.

  The first invention is a multi-stage transmission, wherein (a) a first intermediate output path for transmitting rotation of an input member at a predetermined fixed gear ratio, and a gear ratio larger than the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmitting the rotation of the input member at a lower rotation than the first intermediate output path; and (b) a 2-1 planetary gear device and a 2-2 planet. A part of the sun gear, carrier, and ring gear of the gear device and the second to third planetary gear devices are connected to each other to constitute five rotating elements, and the rotational speed of the five rotating elements is represented by a straight line. When the five rotation elements on the nomograph can be changed from one end to the other end in order, the first rotation element, the second rotation element, the third rotation element, the fourth rotation element, and the fifth rotation element , The first rotating element is selective by the first brake The rotation is stopped, the second rotation element is selectively stopped by the second brake, the third rotation element is selectively stopped by the third brake, and the first rotation element is passed through the first clutch. The fifth rotary element is selectively connected to the second intermediate output path, the fifth rotating element is selectively connected to the second intermediate output path via a second clutch, and the first rotating element is connected to the second intermediate output path via a third clutch. The first rotary output is selectively connected to the first intermediate output path, the third rotary element is selectively connected to the first intermediate output path via the fourth clutch, and the fourth rotary element is connected to the output member to output rotation. And (c) a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake.

  The second invention is the multi-stage transmission according to the first invention. (A) Any of the 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit is provided. (B) the first rotating element is a sun gear of the 2-1 planetary gear device, the second rotating element is a carrier of the 2-1 planetary gear device connected to each other; The ring gear of the 2-2 planetary gear device, the ring gear of the 2-1 planetary gear device, and the ring gear of the 2-1 planetary gear device, the ring gear of the 2-1 planetary gear device, the ring gear of the 2-1 planetary gear device connected to each other, A carrier of the apparatus, and a carrier of the 2-3 planetary gear apparatus, wherein the fourth rotating element is a sun gear of the 2-3 planetary gear apparatus, and the fifth rotating element is of the 2-2 planetary gear apparatus. It is a sun gear.

  According to a third aspect of the present invention, in the multi-stage transmission according to the first aspect, (a) any of the 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit is provided. (B) the first rotating element is a ring gear of the 2-1 planetary gear device, and the second rotating element is a carrier of the 2-1 planetary gear device connected to each other; The carrier of the 2-2 planetary gear device and the second-3 planetary gear of the 2-2 planetary gear device, the ring gear of the 2-2 planetary gear device, and the ring gear of the 2-3 planetary gear device, wherein the third rotating element is connected to each other. The fourth rotating element is a sun gear of the second to third planetary gear device, and the fifth rotating element is a sun gear of the 2-1 planetary gear device and the second to second planets connected to each other. The sun gear of the gear unit And features.

  A fourth invention is the multi-stage transmission according to the first invention, wherein (a) the 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit are all (B) the first rotating element is a sun gear of the 2-1 planetary gear device, and the second rotating element is a ring gear of the 2-2 planetary gear device connected to each other; The ring gear of the 2-3 planetary gear device, wherein the third rotating element is the carrier of the 2-2 planetary gear device and the carrier of the 2-3 planetary gear device connected to each other, and the fourth rotating element is mutually connected The fifth rotating element is connected to the ring gear of the 2-1 planetary gear device and the second gear of the 2-1 planetary gear device connected to each other, and the fifth rotating element is connected to the sun gear of the 2-3 planetary gear device. -2 of planetary gear unit Characterized in that it is a Ngiya.

  A fifth aspect of the invention is the multi-stage transmission according to the first aspect of the invention, in which (a) the 2-1 planetary gear unit, the 2-2 planetary gear unit, and the 2-3 planetary gear unit of the second transmission unit are all. (B) the first rotating element is a sun gear of the second-3 planetary gear device, the second rotating element is a ring gear of the 2-1 planetary gear device, and the third rotating element Is a carrier of the 2-1 planetary gear device and a ring gear of the 2-2 planetary gear device connected to each other, and the fourth rotating element is a carrier of the 2-2 planetary gear device and the carrier of the 2-2 planetary gear device connected to each other. The carrier of the 2-3 planetary gear device, wherein the fifth rotating element is connected to the sun gear of the 2-1 planetary gear device, the sun gear of the 2-2 planetary gear device, and the 2-3 planetary gear. The ring gear of the gear unit And features.

  A sixth aspect of the present invention is the multi-stage transmission according to the first aspect, wherein (a) the 2-1 planetary gear unit of the second transmission unit is a double pinion type, the 2-2 planetary gear unit is a single pinion type, The 2-3 planetary gear device is a single pinion type, and (b) the first rotating element is a sun gear of the 2-2 planetary gear device and a sun gear of the 2-3 planetary gear device connected to each other, The second rotating element is a carrier of the 2-1 planetary gear device and the carrier of the 2-2 planetary gear device that are connected to each other, and the third rotating element is the 2-2 planetary gear device that is connected to each other. And the fourth rotating element is a ring gear of the 2-1 planetary gear device and a ring gear of the 2-3 planetary gear device, which are connected to each other. 5 rotations required It is characterized in that it is a sun gear of the first 2-1 planetary gear device.

  A seventh aspect of the present invention is the multi-stage transmission according to the first aspect, wherein (a) the 2-1 planetary gear unit, the 2-2 planetary gear unit, and the 2-3 planetary gear unit of the second transmission unit are all (B) the first rotating element is a sun gear of the 2-1 planetary gear device, the second rotating element is a ring gear of the 2-2 planetary gear device, and the third rotating element Is the carrier of the 2-2 planetary gear device and the ring gear of the 2-3 planetary gear device connected to each other, and the fourth rotating element is the carrier of the 2-1 planetary gear device connected to each other, The ring gear of the 2-1 planetary gear unit and the second-3 planetary unit, wherein the fifth rotating element is connected to each other by the sun gear of the 2-2 planetary gear unit and the carrier of the 2-3 planetary gear unit. The sun gear of the gear unit And features.

  According to an eighth aspect of the invention, (a) a first intermediate output path for transmitting rotation of the input member at a predetermined fixed gear ratio, and a gear ratio larger than that of the first intermediate output path, the rotation of the input member is A first transmission unit having a second intermediate output path that transmits at a lower rotation than the first intermediate output path; and (b) a single pinion type 2-1 planetary gear device and a 2-2 planetary gear. Device, and a 2-3 planetary gear device, the first rotating element is constituted by the sun gear of the 2-1 planetary gear device, the carrier of the 2-1 planetary gear device, and the 2-2 planetary gear device. Ring gear and the ring gear of the 2-3 planetary gear device are connected to each other to form a second rotating element, and the ring gear of the 2-1 planetary gear device, the carrier of the 2-2 planetary gear device, and the 2- The carriers of the three planetary gear units are connected to each other The third rotating element is configured, the fourth rotating element is configured by the sun gear of the 2-3 planetary gear device, the fifth rotating element is configured by the sun gear of the 2-2 planetary gear device, and the first rotation The element is selectively stopped by the first brake, the second rotating element is selectively stopped by the second brake, the third rotating element is selectively stopped by the third brake, and the first The rotating element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotating element is selectively connected to the second intermediate output path via a second clutch. Is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, and the fourth rotating element is an output. Connect to member And (c) a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake.

  The ninth aspect of the present invention is: (a) a first intermediate output path for transmitting rotation of the input member at a predetermined fixed gear ratio; and a gear ratio larger than the first intermediate output path; A first transmission unit having a second intermediate output path that transmits at a lower rotation than the first intermediate output path; and (b) a single pinion type 2-1 planetary gear device and a 2-2 planetary gear. Device, and a 2-3 planetary gear device, the first rotating element is constituted by the ring gear of the 2-1 planetary gear device, the carrier of the 2-1 planetary gear device, and the 2-2 planetary gear device. The ring gear of the second planetary gear unit and the ring gear of the second to third planetary gear units are connected to each other to form a second rotating element, and the carrier of the second to second planetary gear unit and the carrier of the second to third planetary gear unit are connected to each other. The third rotation element is configured, and the second-3 The fourth rotating element is constituted by the sun gear of the star gear device, the sun gear of the 2-1 planetary gear device and the sun gear of the 2-2 planetary gear device are connected to each other to constitute the fifth rotating element, The one rotation element is selectively stopped by the first brake, the second rotation element is selectively stopped by the second brake, the third rotation element is selectively stopped by the third brake, The first rotating element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotating element is selectively connected to the second intermediate output path via a second clutch, The rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, and the fourth rotating element Out A second speed changer coupled to the force member for outputting rotation; and (c) a plurality of shift speeds are established by switching the engagement and release states of the clutch and brake. .

  In the tenth aspect of the invention, (a) a first intermediate output path that transmits the rotation of the input member at a predetermined fixed gear ratio, and a gear ratio larger than the first intermediate output path, the rotation of the input member is A first transmission unit having a second intermediate output path that transmits at a lower rotation than the first intermediate output path; and (b) a single pinion type 2-1 planetary gear device and a 2-2 planetary gear. Device, and a 2-3 planetary gear device, the first rotating element is constituted by the sun gear of the 2-1 planetary gear device, and the ring gear and the 2-3 planetary gear device of the 2-2 planetary gear device. Ring gears are connected to each other to form a second rotating element, and the carrier of the 2-2 planetary gear device and the carrier of the 2-3 planetary gear device are connected to each other to form a third rotating element. 1 planetary gear carrier and 2nd The sun gear of the planetary gear device is connected to each other to constitute a fourth rotating element, and the ring gear of the 2-1 planetary gear device and the sun gear of the 2-2 planetary gear device are connected to each other to constitute a fifth rotating element. The first rotating element is selectively stopped by the first brake, the second rotating element is selectively stopped by the second brake, and the third rotating element is selectively rotated by the third brake. The first rotating element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotating element is selectively connected to the second intermediate output path via a second clutch. The first rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, First The four-rotation element has a second transmission unit that is coupled to the output member and outputs rotation, and (c) a plurality of shift stages are established by switching between engagement and disengagement of the clutch and brake. It is characterized by.

  In an eleventh aspect of the invention, (a) a first intermediate output path for transmitting rotation of the input member at a predetermined fixed gear ratio, and a gear ratio larger than the first intermediate output path, the rotation of the input member is A first transmission unit having a second intermediate output path that transmits at a lower rotation than the first intermediate output path; and (b) a single pinion type 2-1 planetary gear device and a 2-2 planetary gear. And a 2-3 planetary gear device, the first rotating element is constituted by the sun gear of the 2-3 planetary gear device, and the second rotating element is constituted by the ring gear of the 2-1 planetary gear device. The carrier of the 2-1 planetary gear device and the ring gear of the 2-2 planetary gear device are connected to each other to form a third rotating element, and the carrier of the 2-2 planetary gear device and the 2-3 planetary gear device. The four carriers are connected to each other The fifth rotating element is configured by connecting the sun gear of the 2-1 planetary gear device, the sun gear of the 2-2 planetary gear device, and the ring gear of the 2-3 planetary gear device to each other. In addition, the first rotating element is selectively stopped by the first brake, the second rotating element is selectively stopped by the second brake, and the third rotating element is selectively stopped by the third brake. The first rotating element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotating element is selectively connected to the second intermediate output path via a second clutch. The first rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, 4 rotation elements A second speed changer coupled to the output member for outputting rotation; and (c) a plurality of shift speeds are established by switching between engagement and release states of the clutch and brake. .

  In a twelfth aspect of the invention, (a) a first intermediate output path for transmitting rotation of the input member at a predetermined fixed gear ratio, and a gear ratio larger than the first intermediate output path, the rotation of the input member is A first transmission unit including a second intermediate output path that transmits at a lower rotation than the first intermediate output path; and (b) a double pinion type 2-1 planetary gear device, a single pinion type 2-2. A planetary gear unit and a single-pinion type second to third planetary gear unit are provided, and the sun gear of the second to second planetary gear unit and the sun gear of the second to third planetary gear unit are connected to each other to form a first rotating element. And the carrier of the 2-1 planetary gear device and the carrier of the 2-2 planetary gear device are connected to each other to form the second rotating element, and the ring gear of the 2-2 planetary gear device and the second-3 The planetary gear set carriers Are connected to each other to form a third rotating element, and a ring gear of the 2-1 planetary gear device and a ring gear of the 2-3 planetary gear device are connected to each other to form a fourth rotating element, and the 2-1 planetary gear is configured. The sun gear of the device constitutes the fifth rotating element, the first rotating element is selectively stopped by the first brake, the second rotating element is selectively stopped by the second brake, The three-rotation element is selectively stopped by the third brake, the first rotation element is selectively connected to the second intermediate output path through the first clutch, and the fifth rotation element is connected to the second clutch. Selectively connected to the second intermediate output path, the first rotating element is selectively connected to the first intermediate output path via a third clutch, and the third rotating element is connected to the first intermediate output path via a fourth clutch. First A second transmission unit selectively connected to the intermediate output path, and the fourth rotation element connected to the output member to output rotation; and (c) engaging and releasing the clutch and the brake. A plurality of shift speeds are established by switching.

  In the thirteenth invention, (a) a first intermediate output path for transmitting the rotation of the input member at a predetermined fixed gear ratio, and a gear ratio larger than the first intermediate output path, the rotation of the input member is A first transmission unit having a second intermediate output path that transmits at a lower rotation than the first intermediate output path; and (b) a single pinion type 2-1 planetary gear device and a 2-2 planetary gear. And a 2-3 planetary gear device, the first rotating element is constituted by the sun gear of the 2-1 planetary gear device, and the second rotating element is constituted by the ring gear of the 2-2 planetary gear device. The carrier of the 2-2 planetary gear device and the ring gear of the 2-3 planetary gear device are connected to each other to form a third rotating element, and the carrier of the 2-1 planetary gear device, the 2-2 planetary gear. Sun gear of device, and 2-3 planetary teeth The carrier of the device is connected to each other to form the fourth rotating element, and the ring gear of the 2-1 planetary gear device and the sun gear of the 2-3 planetary gear device are connected to each other to form the fifth rotating element. The first rotating element is selectively stopped by the first brake, the second rotating element is selectively stopped by the second brake, and the third rotating element is selectively stopped by the third brake. A first rotating element is selectively connected to the second intermediate output path via a first clutch, and a fifth rotating element is selectively connected to the second intermediate output path via a second clutch; The first rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, Rotation required And a second transmission section connected to the output member for outputting rotation, and (c) a plurality of shift stages are established by switching between engagement and release states of the clutch and brake. And

  A fourteenth aspect of the present invention is the multi-stage transmission according to any one of the first to thirteenth aspects of the invention, in which (a-1) the largest speed ratio established when the second clutch and the third brake are engaged. (A-2) a second shift stage having a gear ratio smaller than that of the first shift stage, which is established by engaging the second clutch and the second brake; A third shift speed established by engaging the second clutch and the first brake and having a gear ratio smaller than that of the second shift speed; (a-4) engaging the first clutch and the second clutch; (A-5) established by engaging the second clutch and the third clutch, the fourth gear having a gear ratio smaller than that of the third gear. The gear ratio is smaller than 4th gear. (A-6) a sixth shift stage that is established by engaging the second clutch and the fourth clutch and has a smaller gear ratio than the fifth shift stage, (a-7) A seventh shift stage having a gear ratio smaller than that of the sixth shift stage, which is established when the third clutch and the fourth clutch are engaged; (a-8) the first clutch and the fourth clutch are engaged; An eighth shift stage having a gear ratio smaller than the seventh shift stage, (a-9) established by engaging the fourth clutch and the first brake. The shift is performed using seven or more shift stages among the ninth shift stages having a gear ratio smaller than that of the shift stages.

  The gear ratio is a gear ratio of the entire multi-stage transmission including the first transmission unit and the second transmission unit, and is (rotational speed of the input member / rotational speed of the output member).

  A fifteenth aspect of the present invention is the multi-stage transmission according to any one of the first to fourteenth aspects of the present invention, wherein the first shift stage in the reverse rotation direction that is established when the first clutch and the third brake are engaged, Shifting is performed using at least one of the second speeds in the reverse rotation direction established by engaging one clutch and the second brake.

  A sixteenth aspect of the present invention is the multi-stage transmission according to any one of the first to fifteenth aspects of the present invention, wherein the first transmission unit includes a first planetary gear unit and any one of the three rotating elements of the first planetary gear unit. One of them is connected to the input member and is rotationally driven, the other one is fixed to be non-rotatable, and the other one is configured to be transmitted to the input member by being decelerated and rotated as an intermediate output member, A path for transmitting through the intermediate output member is the second intermediate output path, and a path for transmitting the rotation of the input member as it is at a gear ratio of 1.0 is the first intermediate output path.

  According to the multi-stage transmission of the present invention, it is possible to perform a multi-stage shift of seven or more stages in the forward rotation direction and to establish a plurality of shift stages in the reverse rotation direction. Since the first transmission unit having the intermediate output path and the second transmission unit having the three planetary gear units can achieve the multi-stage transmission by switching the engagement of the four clutches and the three brakes, it is lightweight and compact. In addition, since the shift can be performed by holding the two engaging elements (clutch or brake), the shift control is easy and the occurrence of shift shock is suppressed.

  In the second to thirteenth inventions specifically defined for the first to fifth rotating elements, the gear ratio ρ of the three planetary gear units of the second transmission unit is about 0.3 to 0.7. By appropriately determining within the range, it is possible to set the gear ratios of the seven or more gear stages in a form close to the equivalent ratio while using a relatively small (small diameter) planetary gear device. In addition, a large gear ratio range of, for example, about 6 or more can be secured in total, and the present invention is preferably applied to a vehicle multi-stage transmission. It is possible to establish a plurality of shift speeds in the reverse rotation direction, and by selecting a shift speed with an appropriate gear ratio or shifting using a plurality of shift speeds that are easy to shift, a multi-speed shift for vehicles It is suitably applied to the machine.

  The present invention is suitably applied to an automatic transmission for a vehicle. For example, rotation is input from a driving source such as an internal combustion engine through a fluid coupling such as a torque converter, and a gear is changed at a predetermined gear ratio to output gears or outputs. It is transmitted from the output member such as the shaft to the left and right drive wheels via the differential gear device, but can also be applied to automatic transmissions other than those for vehicles. The input member is, for example, a turbine shaft of a torque converter.

  The mounting position of the automatic transmission with respect to the vehicle is such that the axis of the automatic transmission is the front-rear direction of the vehicle even in a horizontal type such as an FF (front engine / front drive) vehicle where the axis of the automatic transmission is the width direction of the vehicle. It may be a vertical installation type such as an FR (front engine / rear drive) vehicle.

  The automatic transmission may be one that automatically switches the gear position according to the operating state such as the accelerator operation amount or the vehicle speed, but may be one that switches the gear position according to a driver's switch operation (up / down operation or the like). The multi-stage transmission according to the present invention is capable of multi-stage transmission of 7 or more forwards in the forward rotation direction, and is preferably applied to a multi-stage transmission of 8 forwards or 9 forwards. In the case of a nine-speed shift, it is desirable to use the first to ninth shift speeds of the fourteenth aspect of the invention as they are, and for a seven-speed shift or an eight-speed shift, any 7 of the first to ninth shift speeds. One or eight shift speeds can be used. For example, in the seven-speed shift, it is desirable to use the first to seventh shift speeds of the fourteenth aspect of the invention, and in the eight-speed shift, the first to seventh shift speeds. In addition to the above, it is desirable to use the eighth shift stage or the ninth shift stage. It should be noted that the present invention can also be used as a multi-stage transmission of six or less stages that performs a shift using six or less of the first to ninth shift stages of the fourteenth invention.

  In the present invention, it is also possible to establish a tenth shift stage having a gear ratio smaller than that of the ninth shift stage by engaging the fourth clutch and the second brake. Shifting can also be performed using the shift speed.

  Regarding the reverse shift speed that is the reverse rotation direction, the first shift speed and the second shift speed of the fifteenth aspect of the invention are possible, but in addition, the third clutch and the third brake can be engaged, The third clutch and the second brake can be engaged to establish a reverse rotational speed, and one or two or more speeds can be appropriately selected according to a desired speed ratio or the like.

  As the first clutch to the fourth clutch and the first brake to the third brake, a hydraulic friction engagement device such as a multi-plate type, a single plate type, or a belt type that is frictionally engaged by a hydraulic cylinder is preferably used. Other types of engagement devices, such as equations, can also be employed. In order to facilitate shift control, a one-way clutch may be provided in parallel with the brakes and clutches. For example, if a one-way clutch is provided in parallel with the third brake, the first shift stage can be established simply by engaging the second clutch, and the second shift stage can be switched simply by engaging the second brake. Can do. When the engine brake is not necessary, a one-way clutch may be provided instead of the third brake. The one-way clutch has the same function as the brake in that it stops rotating. In addition, various modes such as providing a brake and a one-way clutch connected in series in parallel with the second brake are possible.

  In the sixteenth aspect of the invention, the first transmission unit includes the first planetary gear device, and the transmission gear ratio of the second intermediate output path of the first transmission unit (= input rotation speed / output rotation speed of the first transmission unit). Is greater than 1.0 and the rotation of the input member is decelerated and transmitted, while the first intermediate output path transmits the rotation of the input member as it is (speed ratio = 1.0). The transmission ratio of the first intermediate output path is not necessarily 1.0. For example, the transmission ratio of the first intermediate output path is smaller than 1.0 and the rotation of the input member is accelerated and transmitted. Various modes are possible, such as the transmission ratio of the two intermediate output paths being 1.0 and the rotation of the input member being transmitted as it is. The first planetary gear device is disposed coaxially with the second transmission unit, for example.

  As the first planetary gear device of the sixteenth invention, a double pinion type or single pinion type planetary gear device having a sun gear, a carrier and a ring gear as three rotating elements is preferably used. Any one of the ring gear and the ring gear is connected to the input member and driven to rotate, the other one is fixed to be non-rotatable, and the other one is output as an intermediate output member that is decelerated and rotated with respect to the input member. Composed.

  When a single-pinion type planetary gear device is used, a stepped gear having a large-diameter portion and a small-diameter portion (compound planetary gear device) can be adopted as the pinion gear disposed on the carrier. In that case, in addition to the case where the three rotating elements are constituted by a sun gear and a ring gear and a carrier meshed with one and the other of the large diameter part and the small diameter part of the pinion gear, they mesh with the large diameter part and the small diameter part of the pinion gear, respectively. Or a pair of small-diameter sun gears and large-diameter sun gears and a carrier, or a pair of large-diameter ring gears and small-diameter ring-and-gear gears and carriers respectively engaged with the large-diameter portion and small-diameter portion of the pinion gear. .

  In the sixteenth aspect of the invention, the first transmission unit is configured to include the first planetary gear unit. However, the first transmission unit can be configured using a parallel shaft type transmission, and various other modes are available. Is possible. As the parallel shaft type first transmission unit, for example, (a) a first axis to which rotation is input from the input member, and a second axis in which the second transmission unit is disposed in parallel with the first axis. (B) the rotation input from the input member to the first axis side is a predetermined first speed ratio (= rotation speed on the first axis side / second A first power transmission mechanism that transmits to the second axis side at a rotation speed on the axis line side), and (c) a second rotation that is input from the input member to the first axis side that is greater than the first gear ratio. And a second power transmission mechanism that transmits to the second axis side at a gear ratio. In this case, (d) a path that transmits through the first power transmission mechanism is the first intermediate output path. Correspondingly, a path for transmission through the second power transmission mechanism corresponds to the second intermediate output path.

  The first power transmission mechanism and the second power transmission mechanism that transmit power from the first axis side to the second axis side are configured by using, for example, a counter gear pair. Other than pulleys and belts, sprockets, chains, and the like It is also possible to adopt a transmission mechanism.

  The first power transmission mechanism is configured to transmit the rotation on the first axis side to the second axis side as it is, for example, when the first speed ratio is 1.0, and the second speed ratio of the second power transmission mechanism is Is configured to decelerate and transmit the rotation on the first axis side to the second axis side. The first gear ratio of the first power transmission mechanism may be other than 1.0, for example, it is smaller than 1.0 and is configured to accelerate the rotation on the first axis side and transmit it to the second axis side. The second power transmission mechanism is configured to transmit the second power transmission mechanism to the second axis side with a second speed ratio larger than the first speed ratio, for example, 1.0.

  The second transmission unit is configured, for example, as in the second to thirteenth inventions, but other connection forms may be employed.

  The positional relationship between the 2nd-1 planetary gear device to the 2nd-3 planetary gear device of the second transmission unit is not particularly limited. For example, the 2nd-1 planetary gear device, the 2nd-2 planetary gear device, the 2nd-3. Although it can be arranged in the axial direction in the order of the planetary gear device, various aspects are possible, such as the arrangement of the 2-1 planetary gear device and the 2-3 planetary gear device in the center of the axial direction. It is. The clutch and the brake can be variously arranged, for example, concentrated on one end portion or separately arranged on both sides of the planetary gear device.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 (a) is a skeleton diagram of a vehicular automatic transmission 10 as a multi-stage transmission which is an embodiment of the first invention, the second invention, the eighth invention, and the fourteenth invention to the sixteenth invention. b) is an operation table for explaining engaging elements and gear ratios when a plurality of shift speeds are established. The vehicle automatic transmission 10 is preferably used for vertical installation of an FR vehicle or the like, and includes a first transmission unit 14 mainly composed of a double-pinion type first planetary gear unit 12, and a single pinion. Type second planetary gear unit 16, single pinion type third planetary gear unit 18, and second pinion type fourth planetary gear unit 20, and a second transmission unit 22 mainly composed of an input shaft The rotation of 24 is changed and output from the output shaft 26. The input shaft 24 corresponds to an input member, and is a turbine shaft of the torque converter 28. The input shaft 24 receives rotation from the crankshaft 30 of the internal combustion engine as a driving source for traveling through the torque converter 28, while the output shaft 26 Corresponds to an output member, and drives the left and right drive wheels to rotate through, for example, a propeller shaft or a differential gear device. The second planetary gear device 16 corresponds to a 2-1 planetary gear device, the third planetary gear device 18 corresponds to a 2-2 planetary gear device, and the fourth planetary gear device 20 corresponds to a 2-3 planetary gear device. It corresponds to a device. The automatic transmission 10 for a vehicle is configured substantially symmetrically with respect to the center line, and the lower half of the center line is omitted in FIG. The same applies to the following embodiments.

  The carrier CA1 of the first planetary gear unit 12 constituting the first transmission unit 14 is connected to the input shaft 24 and driven to rotate. The sun gear S1 is fixed to the case 32 so as not to rotate, and the ring gear R1 is The intermediate output member is decelerated and rotated with respect to the input shaft 24 and is transmitted to the second transmission unit 22. In the present embodiment, the path for transmitting the rotation of the input shaft 24 to the second transmission unit 22 as it is is the first intermediate output path PA1 for transmitting at a predetermined constant speed ratio (= 1.0), and the input shaft The transmission ratio from the carrier 24 through the carrier CA1, the pinion gear disposed in the carrier CA1, and the ring gear R1 as an intermediate output member to the second transmission 22 is larger than the first intermediate output path PA1 (> 1). .0) is a second intermediate output path PA2 that transmits the rotation of the input shaft 24 at a reduced speed (deceleration). The first intermediate output path PA1 includes a direct connection path PA1a that transmits from the input shaft 24 to the second transmission unit 22 without passing through the first planetary gear device 12, and a carrier CA1 of the first planetary gear device 12 from the input shaft 24. And an indirect path PA <b> 1 b that is transmitted to the second transmission unit 22.

  The second planetary gear device 16, the third planetary gear device 18, and the fourth planetary gear device 20 constituting the second transmission unit 22 are partially connected to each other to thereby form five rotating elements RM1 to RM1. Specifically, the first rotating element RM1 is configured by the sun gear S2 of the second planetary gear unit 16, and the carrier CA2 of the second planetary gear unit 16 and the ring gear R3 of the third planetary gear unit 18 are configured. , And the ring gear R4 of the fourth planetary gear unit 20 are connected to each other to form the second rotating element RM2, and the ring gear R2 of the second planetary gear unit 16, the carrier CA3 of the third planetary gear unit 18, and the fourth planetary gear unit. The carrier CA4 of the device 20 is connected to each other to form a third rotating element RM3. The sun gear S4 of the fourth planetary gear device 20 causes the fourth rotating element RM4 to be connected. Made is, the fifth rotary element RM5 is constituted by a sun gear S3 of the third planetary gear unit 18.

  Then, the first rotation element RM1 (sun gear S2) is selectively connected to the case 32 by the first brake B1 to stop the rotation, and the second rotation element RM2 (carrier CA2 and ring gears R3, R4) is the second brake B2. The third rotation element RM3 (ring gear R2 and carriers CA3 and CA4) is selectively connected to the case 32 by the third brake B3 and is stopped from rotating. The first rotation element RM1 (sun gear S2) is selectively connected to the ring gear R1 of the first planetary gear device 12, which is an intermediate output member, that is, the second intermediate output path PA2, via the first clutch C1, and the fifth rotation element RM5. (Sun gear S3) is also ring gear R1, that is, second intermediate output path PA via second clutch C2. The first rotating element RM1 (sun gear S2) is selectively connected to the carrier CA1 of the first planetary gear unit 12, that is, the indirect path PA1b of the first intermediate output path PA1 via the third clutch C3. The third rotation element RM3 (ring gear R2 and carriers CA3 and CA4) is selectively connected to the input shaft 24, that is, the direct connection path PA1a of the first intermediate output path PA1 via the fourth clutch C4, and the fourth rotation element RM4 (sun gear S4) is integrally connected to the output shaft 26 to output rotation. Each of the first brake B1 to the third brake B3 and the first clutch C1 to the fourth clutch C4 is a multi-plate type hydraulic friction engagement device that is frictionally engaged by a hydraulic cylinder.

  FIG. 2 is a collinear diagram in which the rotational speeds of the rotating elements of the first transmission unit 14 and the second transmission unit 22 can be represented by straight lines. The lower horizontal line is the rotational speed “0” and the upper horizontal line Is the rotational speed “1.0”, that is, the same rotational speed as the input shaft 24. Further, each vertical line of the first transmission unit 14 represents the sun gear S1, the ring gear R1, and the carrier CA1 in order from the left side, and these intervals are the gear ratio of the first planetary gear unit 12 (= the number of teeth of the sun gear). / Number of teeth of ring gear) ρ1. The figure shows a case where the gear ratio ρ1 = 0.500. The five vertical lines of the second transmission unit 22 indicate the first rotation element RM1 (sun gear S2), the second rotation element RM2 (carrier CA2 and ring gears R3 and R4), and the third rotation element RM3 (ring gear R2) in order from the left side. And the carrier CA3, CA4), the fourth rotating element RM4 (sun gear S4), and the fifth rotating element RM5 (sun gear S3), and their intervals are the gear ratio ρ2 of the second planetary gear unit 16, the third planetary gear. It is determined according to the gear ratio ρ3 of the gear unit 18 and the gear ratio ρ4 of the fourth planetary gear unit 20. The figure shows a case where the gear ratio ρ2 = 0.379, ρ3 = 0.292, and ρ4 = 0.704. Note that the circled numbers “1” to “5” of the second transmission unit 22 represent the first rotation element RM1 to the fifth rotation element RM5, respectively. The same applies to the following embodiments.

  Then, as is apparent from this nomograph, the second clutch C2 and the third brake B3 are engaged, and the fifth rotation element RM5 is decelerated and rotated via the first transmission unit 14 and the third rotation. When the rotation of the element RM3 is stopped, the fourth rotation element RM4 connected to the output shaft 26 is rotated at the rotation speed indicated by “1st”, and the largest gear ratio (= the rotation speed of the input shaft 24 / the output shaft 26). 1st speed stage “1st” is established. When the second clutch C2 and the second brake B2 are engaged and the fifth rotating element RM5 is decelerated and rotated via the first transmission unit 14 and the second rotating element RM2 is stopped from rotating, the fourth rotation is performed. The element RM4 is rotated at the rotation speed indicated by “2nd”, and the second speed “2nd” having a smaller gear ratio than the first speed “1st” is established. When the second clutch C2 and the first brake B1 are engaged and the fifth rotating element RM5 is decelerated and rotated through the first transmission unit 14 and the first rotating element RM1 is stopped from rotating, the fourth rotation is performed. The element RM4 is rotated at the rotational speed indicated by “3rd”, and the third speed “3rd” having a smaller gear ratio than the second speed “2nd” is established. When the first clutch C1 and the second clutch C2 are engaged and the second transmission unit 22 is integrally decelerated and rotated through the first transmission unit 14, the fourth rotation element RM4 is indicated by “4th”. The fourth speed “4th”, which is rotated at the rotational speed and has a smaller speed ratio than the third speed “3rd”, is established. When the second clutch C2 and the third clutch C3 are engaged, the fifth rotating element RM5 is decelerated and rotated via the first transmission unit 14, and the first rotating element RM1 is rotated integrally with the input shaft 24. The fourth rotation element RM4 is rotated at the rotational speed indicated by “5th”, and the fifth shift stage “5th” having a smaller gear ratio than the fourth shift stage “4th” is established. When the second clutch C2 and the fourth clutch C4 are engaged, the fifth rotation element RM5 is decelerated and rotated via the first transmission unit 14, and the third rotation element RM3 is rotated integrally with the input shaft 24. The fourth rotation element RM4 is rotated at the rotation speed indicated by “6th”, and the sixth shift stage “6th” having a smaller gear ratio than the fifth shift stage “5th” is established. When the third clutch C3 and the fourth clutch C4 are engaged and the second transmission unit 22 is rotated integrally with the input shaft 24, the fourth rotational element RM4 has a rotational speed indicated by "7th", that is, the input shaft 24 and The seventh shift stage “7th”, which is rotated at the same rotational speed and has a smaller gear ratio than the sixth shift stage “6th”, is established. The gear ratio of the seventh gear stage “7th” is 1. When the first clutch C1 and the fourth clutch C4 are engaged, the first rotating element RM1 is decelerated and rotated via the first transmission unit 14, and the third rotating element RM3 is rotated integrally with the input shaft 24. The fourth rotation element RM4 is rotated at the rotation speed indicated by “8th”, and the eighth shift stage “8th” having a smaller speed ratio than the seventh shift stage “7th” is established. When the fourth clutch C4 and the first brake B1 are engaged and the third rotating element RM3 is rotated integrally with the input shaft 24 and the first rotating element RM1 is stopped from rotating, the fourth rotating element RM4 is “ The ninth shift speed “9th”, which is rotated at the rotation speed indicated by “9th” and has a smaller gear ratio than the eighth shift speed “8th”, is established.

  Further, when the first clutch C1 and the third brake B3 are engaged, the first rotating element RM1 is decelerated and rotated via the first transmission unit 14, and the third rotating element RM3 is stopped from rotating. The fourth rotation element RM4 is reversely rotated at the rotation speed indicated by “Rev1”, and the first reverse shift stage “Rev1” having the largest speed ratio in the reverse rotation direction is established. When the first clutch C1 and the second brake B2 are engaged, the first rotating element RM1 is decelerated and rotated via the first transmission unit 14 and the second rotating element RM2 is stopped from rotating. The rotation element RM4 is reversely rotated at the rotation speed indicated by “Rev2”, and the second reverse shift stage “Rev2” having a smaller gear ratio than the first reverse shift stage “Rev1” is established. The first reverse shift stage “Rev1” and the second reverse shift stage “Rev2” correspond to the first shift stage and the second shift stage of claim 15, respectively.

  The operation table in FIG. 1 (b) summarizes the relationship between the above-described shift speeds and the operation states of the clutches C1 to C4 and the brakes B1 to B3. “O” represents engagement, It is liberation. The gear ratio of each gear stage is appropriately determined by the gear ratios ρ1 to ρ4 of the first planetary gear device 12, the second planetary gear device 16, the third planetary gear device 18, and the fourth planetary gear device 20, for example, ρ1 = If 0.500, ρ2 = 0.379, ρ3 = 0.292, ρ4 = 0.704, the gear ratio shown in FIG. 1 (b) is obtained, and the gear ratio step (the gear ratio between the gear stages) is obtained. Ratio) value is substantially appropriate and the total gear ratio range (= 4.817 / 0.719) is as large as about 6.700, and the gear ratios of the reverse gears “Rev1” and “Rev2” are also appropriate. As a whole, an appropriate gear ratio characteristic can be obtained.

  As described above, according to the vehicle automatic transmission 10 of the present embodiment, a total of four sets of planetary gear units 12, 16, 18, 20 and four clutches C1 to C4 and a multi-speed shift of nine forward speeds and two reverse speeds, Since it is obtained by the three brakes B1 to B3, it is configured to be lightweight and compact, and mountability to the vehicle is improved. Moreover, as is clear from FIG. 1 (b), it is possible to perform shifts at each shift stage by simply grasping any two of the clutches C1 to C4 and the brakes B1 to B3. The occurrence of shock is suppressed.

  The gear ratios ρ1 to ρ4 of the four planetary gear devices 12, 16, 18, and 20 are within a range of about 0.3 to 0.7, and the planetary gear devices 12, 16, 18, and 20 are compared. While maintaining a small size (small diameter), the gear ratios of the first gear stage “1st” to the ninth gear stage “9th” can be set in a form close to an equal ratio as shown in FIG. In addition, a large gear ratio range of 6 or more can be secured in total, and the gear ratio of the reverse gear stage “Rev1” is large, so that an appropriate gear ratio characteristic can be obtained as a whole.

  Next, another embodiment of the present invention will be described. In the following embodiments, parts that are substantially the same as those in the above embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

  3 and 4 show one embodiment of the first invention, the third invention, the ninth invention, and the fourteenth to sixteenth inventions. FIG. 3 is a view corresponding to FIG. 1, and FIG. FIG. The vehicular automatic transmission 40 differs from the vehicular automatic transmission 10 of FIGS. 1 and 2 in the configuration of the second transmission unit 42. That is, the first rotating element RM1 is constituted by the ring gear R2 of the second planetary gear unit 16, and the carrier CA2 of the second planetary gear unit 16, the ring gear R3 of the third planetary gear unit 18, and the ring gear of the fourth planetary gear unit 20 R4 is connected to each other to form the second rotating element RM2, and the carrier CA3 of the third planetary gear device 18 and the carrier CA4 of the fourth planetary gear device 20 are connected to each other to form the third rotating element RM3. The sun gear S4 of the planetary gear device 20 constitutes a fourth rotating element RM4, and the sun gear S2 of the second planetary gear device 16 and the sun gear S3 of the third planetary gear device 18 are connected to each other to constitute a fifth rotating element RM5. Yes. The rotary elements RM1 to RM3 and RM5 and the case 32 by the clutches C1 to C4 and the brakes B1 to B3, the input shaft 24, that is, the first intermediate output path PA1, and the ring gear R1 of the first planetary gear unit 12, that is, the second intermediate output path. The connection relationship with PA2 and the connection between the fourth rotating element RM4 and the output shaft 26 are the same as those in the embodiment of FIGS.

  Also in this case, as shown in FIG. 3 (b), according to the same operation table as in FIG. 1 (b), the 9th forward speed and the reverse speed “Rev1” from the first speed “1st” to the ninth speed “9th”. , “Rev2” is established. Further, the gear ratio of each gear stage is appropriately determined by the gear ratios ρ1 to ρ4 of the first planetary gear device 12, the second planetary gear device 16, the third planetary gear device 18, and the fourth planetary gear device 20, for example. If ρ1 = 0.500, ρ2 = 0.597, ρ3 = 0.292, ρ4 = 0.704, the same collinear diagram as in FIG. 2 is obtained as shown in FIG. 4, and FIG. As shown, the same gear ratio as that shown in FIG. 1 (b) can be obtained, and the same effect as the embodiment shown in FIGS. 1 and 2 can be obtained.

  5 and 6 show one embodiment of the first invention, the fourth invention, the tenth invention, and the fourteenth invention to the sixteenth invention. FIG. 5 is a view corresponding to FIG. 1, and FIG. FIG. The vehicular automatic transmission 50 is different from the vehicular automatic transmission 10 of FIGS. 1 and 2 in the configuration of the second transmission unit 52. That is, the first rotating element RM1 is constituted by the sun gear S2 of the second planetary gear unit 16, and the ring gear R3 of the third planetary gear unit 18 and the ring gear R4 of the fourth planetary gear unit 20 are connected to each other to form the second rotating element RM2. And the carrier CA3 of the third planetary gear unit 18 and the carrier CA4 of the fourth planetary gear unit 20 are connected to each other to form the third rotating element RM3, and the carrier CA2 and the fourth planetary unit of the second planetary gear unit 16 are configured. The sun gear S4 of the gear device 20 is connected to each other to form a fourth rotating element RM4, the ring gear R2 of the second planetary gear device 16 and the sun gear S3 of the third planetary gear device 18 are connected to each other, and the fifth rotating element RM5 is It is configured. Further, the vehicle automatic transmission 50 is preferably used for horizontal installation of an FF vehicle or the like, and an output gear 54 that functions as an output member is integrally connected to the fourth rotating element RM4. The rotary elements RM1 to RM3 and RM5 and the case 32 by the clutches C1 to C4 and the brakes B1 to B3, the input shaft 24, that is, the first intermediate output path PA1, and the ring gear R1 of the first planetary gear unit 12, that is, the second intermediate output path. The connection relationship with PA2 is the same as that of the embodiment of FIGS. However, the first rotating element RM1 is connected to the direct connection path PA1a via the third clutch C3, and the third rotating element RM3 is connected to the indirect path PA1b via the fourth clutch C4.

  Also in this case, as shown in FIG. 5 (b), according to the same operation table as FIG. 1 (b), the 9th forward speed and the reverse speed “Rev1” from the first gear stage “1st” to the ninth gear stage “9th”. , “Rev2” is established. Further, the gear ratio of each gear stage is appropriately determined by the gear ratios ρ1 to ρ4 of the first planetary gear device 12, the second planetary gear device 16, the third planetary gear device 18, and the fourth planetary gear device 20, for example. If ρ1 = 0.500, ρ2 = 0.395, ρ3 = 0.292, ρ4 = 0.704, the same collinear diagram as in FIG. 2 is obtained as shown in FIG. 6, and FIG. As shown, the same gear ratio as that shown in FIG. 1 (b) can be obtained, and the same effect as the embodiment shown in FIGS. 1 and 2 can be obtained.

  7 and 8 show one embodiment of the first invention, the fifth invention, the eleventh invention, and the fourteenth to sixteenth inventions. FIG. 7 is a view corresponding to FIG. 1, and FIG. FIG. The vehicle automatic transmission 60 is different from the vehicle automatic transmission 50 of FIGS. 5 and 6 in the configuration of the second transmission unit 62. That is, the first rotating element RM1 is constituted by the sun gear S4 of the fourth planetary gear device 20, the second rotating element RM2 is constituted by the ring gear R2 of the second planetary gear device 16, and the carrier CA2 of the second planetary gear device 16 and The ring gear R3 of the third planetary gear unit 18 is coupled to each other to form a third rotating element RM3, and the carrier CA3 of the third planetary gear unit 18 and the carrier CA4 of the fourth planetary gear unit 20 are coupled to each other to perform the fourth rotation. The element RM4 is configured, and the sun gear S2 of the second planetary gear unit 16, the sun gear S3 of the third planetary gear unit 18, and the ring gear R4 of the fourth planetary gear unit 20 are connected to each other to configure a fifth rotating element RM5. Yes. The rotary elements RM1 to RM3 and RM5 and the case 32 by the clutches C1 to C4 and the brakes B1 to B3, the input shaft 24, that is, the first intermediate output path PA1, and the ring gear R1 of the first planetary gear unit 12, that is, the second intermediate output path. The connection relationship with PA2 and the connection between the fourth rotating element RM4 and the output gear 54 are the same as those in the embodiment of FIGS.

  Also in this case, as shown in FIG. 7 (b), according to the same operation table as in FIG. 1 (b), the 9th forward speed “1st” to 9th speed “9th” and the reverse speed “Rev1”. , “Rev2” is established. Further, the gear ratio of each gear stage is appropriately determined by the gear ratios ρ1 to ρ4 of the first planetary gear device 12, the second planetary gear device 16, the third planetary gear device 18, and the fourth planetary gear device 20, for example. If ρ1 = 0.500, ρ2 = 0.292, ρ3 = 0.710, ρ4 = 0.395, the same collinear diagram as in FIG. 2 is obtained as shown in FIG. 8, and FIG. As shown, the same gear ratio as that shown in FIG. 1 (b) can be obtained, and the same effect as the embodiment shown in FIGS. 1 and 2 can be obtained.

  9 to 11 show one embodiment of the first invention, the sixth invention, the twelfth invention, the fourteenth invention, and the fifteenth invention. FIG. 9 is a skeleton diagram of a vehicle drive device 110 that is suitably used when mounted horizontally on a vehicle such as an FF vehicle, and is an automatic transmission for a vehicle as a multi-stage transmission according to an embodiment of the present invention. FIG. 10 is an operation table for explaining engagement elements and gear ratios when establishing a plurality of shift stages of the vehicular automatic transmission 112. The automatic transmission 112 for a vehicle is disposed across a first axis L1 and a second axis L2 that are parallel to each other. An input shaft 114 is provided on the first axis L1, and power is generated by combustion of fuel. Power is input from an engine 116 such as an internal combustion engine that generates the pressure through a torque converter 118 as a fluid coupling. The input shaft 114 corresponds to an input member and is a turbine shaft of the torque converter 118.

  A first transmission unit 120 is provided across the first axis L1 and the second axis L2, and a second transmission unit 122 is disposed on the second axis L2. The first transmission unit 120 includes a first power transmission mechanism 124 and a second power transmission mechanism 126, and includes two pairs of counter gears 124a and 124b, 126a and 126b meshed with each other. The counter gears 124a and 126a on the first axis L1 side are all disposed so as not to rotate relative to the input shaft 114 by spline fitting or the like, while the counter gears 124b and 126b on the second axis L2 side are arranged around the axis. The counter gears 124a and 126a transmit rotation to the counter gears 124b and 126b at a first speed ratio γ1 and a second speed ratio γ2, respectively. The first speed ratio γ1 (= the number of teeth of the counter gear 124b / the number of teeth of the counter gear 124a) is smaller than the second speed ratio γ2 (= the number of teeth of the counter gear 126b / the number of teeth of the counter gear 126a). Then, when the first speed ratio γ1 = 1.0 and the second speed ratio γ2 = 2.0, the first power transmission mechanism 124 rotates the input shaft 114 in the reverse direction but at the same rotational speed toward the second axis L2. On the other hand, the second power transmission mechanism 126 decelerates the rotation of the input shaft 114 to 1 / γ2, and transmits it to the second axis L2. In the first transmission unit 120, a path that is transmitted via the first power transmission mechanism 124 corresponds to a first intermediate output path, and a path that is transmitted via the second power transmission mechanism 126 corresponds to a second intermediate output path.

  On the other hand, the second transmission unit 122 disposed on the second axis L2 includes a double pinion type first planetary gear device 128, a single pinion type second planetary gear device 130, and a single pinion type third planetary gear device. The apparatus 132 is mainly configured, and five rotating elements RM1 to RM5 are configured by partially connecting each other. Specifically, the sun gear S2 of the second planetary gear unit 130 and the sun gear S3 of the third planetary gear unit 132 are connected to each other to form the first rotating element RM1, and the carrier CA1 and the second planetary gear unit 128 of the first planetary gear unit 128 are configured. The carrier CA2 of the planetary gear unit 130 is connected to each other to form the second rotating element RM2, and the ring gear R2 of the second planetary gear unit 130 and the carrier CA3 of the third planetary gear unit 132 are connected to each other to form the third rotating element RM3. The ring gear R1 of the first planetary gear device 128 and the ring gear R3 of the third planetary gear device 132 are connected to each other to form a fourth rotating element RM4, and the fifth rotation is performed by the sun gear S1 of the first planetary gear device 128. Element RM5 is configured. The first planetary gear device 128 corresponds to a 2-1 planetary gear device, the second planetary gear device 130 corresponds to a 2-2 planetary gear device, and the third planetary gear device 132 corresponds to a 2-3 planetary gear device. It corresponds to a device.

  The first rotating element RM1 (sun gears S2 and S3) is selectively connected to the case 134 by the first brake B1 and stopped rotating, and the second rotating element RM2 (carriers CA1 and CA2) is stopped by the second brake B2. The third rotation element RM3 (the ring gear R2 and the carrier CA3) is selectively connected to the case 134 by the third brake B3 and is stopped from rotating. The first rotation element is selectively connected to the case 134 and stopped. RM1 (sun gears S2, S3) is selectively connected to the counter gear 126b of the second power transmission mechanism 126, which is the second intermediate output path, via the first clutch C1, and the fifth rotation element RM5 (sun gear S1) is Similarly, it is selectively coupled to the counter gear 126b via the second clutch C2, and the first rotating element RM1 (sun gear) 2, S3) is selectively coupled to the counter gear 124b of the first power transmission mechanism 124, which is the first intermediate output path, via the third clutch C3, and the third rotating element RM3 (ring gear R2 and carrier CA3) is Similarly, the counter gear 124b is selectively connected via the fourth clutch C4, and the fourth rotating element RM4 (ring gears R1, R3) is integrally connected to the output gear 136 to output rotation. In the present embodiment, most of the second transmission unit 122 excluding the first brake B1 is disposed between the first power transmission mechanism 124 and the second power transmission mechanism 126 in the axial direction.

  The output gear 136 corresponds to an output member, and meshes with the ring gear 140 of the differential gear device 138 disposed on the third axis L3 parallel to the first axis L1 and the second axis L2 to transmit the rotation. Then, it is distributed to the left and right drive wheels via a pair of axles 142 and 144. FIG. 9 is an expanded view showing that the first axis L1, the second axis L2, and the third axis L3 are located in the same plane. Actually, the first axis L1 to the third axis L3. Are arranged so as to form a triangle in a side view.

  FIG. 11 is a collinear diagram that can represent the rotational speed of each of the rotating elements RM1 to RM5 of the second transmission unit 122 by a straight line. The lower horizontal line is the rotational speed “0”, and the upper horizontal line is 1 /. γ1, that is, “1.0” in the present embodiment, and the intermediate horizontal line is 1 / γ2, that is, “0.5” in the present embodiment. Further, the five vertical lines indicate the first rotating element RM1 (sun gears S2 and S3), the second rotating element RM2 (carriers CA1 and CA2), the third rotating element RM3 (ring gear R2 and carrier CA3) in order from the left side. The fourth rotating element RM4 (ring gears R1 and R3) and the fifth rotating element RM5 (sun gear S1) are shown, and their intervals are the gear ratio ρ1 of the first planetary gear unit 128 and the gears of the second planetary gear unit 130. It is determined according to the ratio ρ2 and the gear ratio ρ3 of the third planetary gear device 132. In the figure, the gear ratios ρ1 = 0.548, ρ2 = 0.379, ρ3 = 0.390, and γ1 = 1.0 and γ2 = 2.0, the second transmission unit 22 of FIG. It will be the same alignment chart.

  Therefore, also in this embodiment, as shown in FIG. 10, the engagement and disengagement states of the clutches C1 to C4 and the brakes B1 to B3 are switched according to the same operation table as in FIG. Nine forward shift stages and reverse shift stages “Rev1” and “Rev2” from 1st to the ninth shift stage “9th” are established. Further, the gear ratios of the respective gear positions are the first gear ratio γ1, the second gear ratio γ2, and the first planetary gear device 128, the second planetary gear device 130, and the third planetary gear device 132. For example, if γ1 = 1.0, γ2 = 2.0, ρ1 = 0.548, ρ2 = 0.379, and ρ3 = 0.390, the gear ratios are determined according to the gear ratios ρ1 to ρ3. The same speed ratio is obtained, and the same effect as the embodiment of FIGS. 1 and 2 is obtained.

  In the present embodiment, the engine 116, the torque converter 118, and counter gears 124a and 126a of the first transmission unit 120 are disposed on the first axis L1, while the first transmission unit 120 is disposed on the second axis L2. Since the second transmission unit 122 having the counter gears 124b and 126b and the three sets of planetary gear devices 128, 130, and 132 is disposed, the shaft is compared with the case where they are disposed on the same axis. The direction dimension can be shortened, and the first axis L1 and the second axis L2 can be mounted horizontally and compactly with respect to the FF vehicle so that the axial direction of the first axis L1 and the second axis L2 is the vehicle width direction.

  The vehicle automatic transmission 150 in FIG. 12 is adjacent to the first power transmission mechanism 124 and the second power transmission mechanism 126 that constitute the first transmission unit 120 in the vehicle automatic transmission 112 in FIG. When the three planetary gear devices 128, 130, 132 of the second transmission unit 122 are disposed on the opposite side of the engine 116 with the first transmission unit 120 interposed therebetween, the first rotating element RM1 (sun gear) S2 and S3) are connected to the clutches C1 and C3 and the brake B1 via a hollow shaft, while the fifth rotating element RM5 (sun gear S1) is connected to the second clutch via an insertion shaft that passes through the hollow shaft. Connected to C2.

  FIGS. 13 to 15 show an embodiment of the first invention, the second invention, the seventh invention, and the thirteenth to fifteenth inventions. FIG. 13 is a view corresponding to FIG. 9, and FIG. FIG. 15 is a diagram corresponding to FIG. The vehicle automatic transmission 160 has positions of the first power transmission mechanism 124 and the second power transmission mechanism 126 of the first transmission unit 120 as compared with the vehicle automatic transmission 112 of the embodiment of FIGS. Is the opposite, and the configuration of the second transmission unit 162 disposed between them is different. The second transmission unit 162 is mainly configured by a single pinion type first planetary gear unit 164, a single pinion type second planetary gear unit 166, and a single pinion type third planetary gear unit 168. The first rotating element RM1 is constituted by the sun gear S1 of the first planetary gear device 164, and the second rotating element RM2 is constituted by the ring gear R2 of the second planetary gear device 166, and the carrier CA2 and the third planetary gear of the second planetary gear device 166 are arranged. The ring gear R3 of the gear device 168 is connected to each other to form a third rotating element RM3. The carrier CA1 of the first planetary gear device 164, the sun gear S2 of the second planetary gear device 166, and the carrier CA3 of the third planetary gear device 168. Are connected to each other to form a fourth rotating element RM4, and the first planetary gear device 164 Fifth rotary element RM5 ring gear R1 and the sun gear S3 of the third planetary gear device 168 is connected to each other is formed. The rotary elements RM1 to RM5 by the clutches C1 to C4 and the brakes B1 to B3, the counter gear 124b of the first power transmission mechanism 124 that is the first intermediate output path, and the second power transmission mechanism 126 that is the second intermediate output path. The counter gear 126b and the case 134 are connected to each other, and the fourth rotating element RM4 is connected to the output gear 136 in the same manner as the embodiment shown in FIGS. The first planetary gear device 164 corresponds to a 2-1 planetary gear device, the second planetary gear device 166 corresponds to a 2-2 planetary gear device, and the third planetary gear device 168 corresponds to a 2-3 planetary gear device. It corresponds to a device.

  Also in this case, as shown in FIG. 14, according to the same operation table as in FIG. 10, the first forward speed “1st” to the ninth forward speed “9th” and the reverse speeds “Rev1” and “Rev2” are established. Be made. Further, the gear ratios of the respective gear stages are the first gear ratio γ1, the second gear ratio γ2, and the first planetary gear device 164, the second planetary gear device 166, and the third planetary gear device 168. For example, if γ1 = 1.0, γ2 = 2.0, ρ1 = 0.395, ρ2 = 0.704, and ρ3 = 0.710, the gear ratios ρ1 to ρ3 are determined as shown in FIG. The same collinear chart as that of FIG. 11 is obtained, and as shown in FIG. 14, the same gear ratio as that of FIG. 10 is obtained, and the same effect as the embodiment of FIGS. 9 to 11 is obtained.

  In each of the above-described embodiments, the case of 9 forward speeds has been described. In any of the above-described embodiments, the first forward speed “1st” to the eighth forward speed “8th” are changed to 8 forward speeds. It is also possible to perform shifts in seven forward speeds from the shift speed “1st” to the seventh shift speed “7th”, and the gear ratio widths in this case are 5.756 and 4.817, respectively. In the eighth forward speed, the second gear shift stage “2nd” to the ninth gear shift stage “9th” are shifted, or the first gear shift stage “1st” to the seventh gear shift stage “7th” + the ninth gear shift stage “9th”. As described above, it is also possible to perform shifting by skipping intermediate shift speeds. As for the seventh forward speed, the speed is changed at the second speed “2nd” to the eighth speed “8th” or the second speed “2nd” to the seventh speed “7th” + the ninth speed “9th”. Various aspects are possible.

  As mentioned above, although the Example of this invention was described in detail based on drawing, these are one embodiment to the last, and this invention is implemented in the aspect which added the various change and improvement based on the knowledge of those skilled in the art. be able to.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure explaining the automatic transmission for vehicles which is one Example of this invention, (a) is a skeleton diagram, (b) is an operation | movement table | surface for establishing each gear stage. FIG. 2 is a collinear diagram of the embodiment of FIG. 1. It is a figure explaining another Example of this invention, and is a case where a 2nd transmission part differs compared with the Example of FIG. 1, and is a figure equivalent to FIG. FIG. 4 is a collinear diagram of the embodiment of FIG. 3. It is a figure explaining another Example of this invention, and is a case where a 2nd transmission part differs compared with the Example of FIG. 1, and is a figure equivalent to FIG. FIG. 6 is a collinear diagram of the embodiment of FIG. 5. It is a figure explaining another Example of this invention, and is a case where a 2nd transmission part differs compared with the Example of FIG. 1, and is a figure equivalent to FIG. FIG. 8 is a collinear diagram of the embodiment of FIG. 7. It is a figure explaining another Example of this invention, and is a case where the 1st transmission part is a counter gear type arrange | positioned ranging over two parallel axes | shafts, and is the whole vehicle drive device containing an engine etc. FIG. It is an operation | movement table | surface of the Example of FIG. FIG. 10 is a collinear diagram of the embodiment of FIG. 9. FIG. 10 is a skeleton diagram showing an embodiment in the case where a first power transmission mechanism and a second power transmission mechanism constituting a first transmission unit are arranged adjacent to each other as compared with FIG. 9. It is a figure explaining another Example of this invention, and is a case where a 2nd transmission part differs compared with the Example of FIG. 9, and is a skeleton diagram equivalent to FIG. It is an operation | movement table | surface of the Example of FIG. FIG. 14 is a collinear diagram of the embodiment of FIG. 13.

Explanation of symbols

  10, 40, 50, 60, 112, 150, 160: Automatic transmission for vehicles (multi-stage transmission) 12: First planetary gear unit 14, 120: First transmission unit 16: Second planetary gear unit (second 2- 18: 3rd planetary gear device (2-2 planetary gear device) 20: 4th planetary gear device (2-3 planetary gear device) 22, 42, 52, 62, 122, 162: 1st planetary gear device) 2 speed change parts 24, 114: input shaft (input member) 26: output shaft (output member) 54, 136: output gear (output member) 124: first power transmission mechanism (first intermediate output path) 126: second power Transmission mechanism (second intermediate output path) 128, 164: first planetary gear device (2-1 planetary gear device) 130, 166: second planetary gear device (2-2 planetary gear device) 132, 168: first 3 planetary teeth Device (second-3 planetary gear device) PA1: first intermediate output path PA2: second intermediate output path RM1: first rotation element RM2: second rotation element RM3: third rotation element RM4: fourth rotation element RM5: Fifth rotating element C1: first clutch C2: second clutch C3: third clutch C4: fourth clutch B1: first brake B2: second brake B3: third brake

Claims (16)

A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
The sun gear, the carrier, and the ring gear of the 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device are connected to each other to form five rotating elements. In the collinear chart in which the rotational speeds of the five rotating elements can be represented by straight lines, the five rotating elements are arranged in order from one end to the other end in the order of the first rotating element, the second rotating element, and the third rotating element. , The fourth rotating element, and the fifth rotating element, the first rotating element is selectively stopped by the first brake, and the second rotating element is selectively stopped by the second brake. The third rotating element is selectively stopped by a third brake, the first rotating element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotating element is Second clutch The first rotating element is selectively connected to the first intermediate output path via a third clutch, and the third rotating element connects the fourth clutch to the second intermediate output path. A second transmission unit that is selectively connected to the first intermediate output path through the fourth rotation element and that is connected to an output member to output rotation;
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. The 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit are all single pinion types,
The first rotating element is a sun gear of the 2-1 planetary gear device, the second rotating element is a carrier of the 2-1 planetary gear device connected to each other, a ring gear of the 2-2 planetary gear device, And the ring gear of the 2-3 planetary gear device, wherein the third rotating element is connected to the ring gear of the 2-1 planetary gear device, the carrier of the 2-2 planetary gear device, and the 2- The carrier of a three planetary gear device, wherein the fourth rotating element is a sun gear of the second to third planetary gear device, and the fifth rotating element is a sun gear of the 2-2 planetary gear device. Item 4. The multi-stage transmission according to Item 1. The 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit are all single pinion types,
The first rotating element is a ring gear of the 2-1 planetary gear device, the second rotating element is a carrier of the 2-1 planetary gear device connected to each other, a ring gear of the 2-2 planetary gear device, In the ring gear of the 2-3 planetary gear device, the third rotating element is the carrier of the 2-2 planetary gear device and the carrier of the 2-3 planetary gear device connected to each other, and the fourth rotation. The element is a sun gear of the 2-3 planetary gear device, and the fifth rotating element is a sun gear of the 2-1 planetary gear device and a sun gear of the 2-2 planetary gear device connected to each other. The multi-stage transmission according to claim 1. The 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit are all single pinion types,
The first rotating element is a sun gear of the 2-1 planetary gear device, and the second rotating element is a ring gear of the 2-2 planetary gear device and a ring gear of the second-3 planetary gear device connected to each other. The third rotating element is a carrier of the 2-2 planetary gear device and a carrier of the second-3 planetary gear device which are connected to each other, and the fourth rotating element is the 2-1 planetary gear connected to each other. The fifth rotating element is a ring gear of the 2-1 planetary gear device and a sun gear of the 2-2 planetary gear device which are connected to each other by a carrier of the gear device and a sun gear of the 2-3 planetary gear device. The multi-stage transmission according to claim 1. The 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit are all single pinion types,
The first rotating element is a sun gear of the 2-3 planetary gear device, the second rotating element is a ring gear of the 2-1 planetary gear device, and the third rotating element is connected to the second 2- The carrier of the first planetary gear unit and the ring gear of the second to second planetary gear unit, wherein the fourth rotating element is connected to each other, the carrier of the second to second planetary gear unit and the carrier of the second to third planetary gear unit The fifth rotating element is a sun gear of the 2-1 planetary gear device, a sun gear of the 2-2 planetary gear device, and a ring gear of the 2-3 planetary gear device that are connected to each other. The multi-stage transmission according to claim 1. The 2-1 planetary gear device of the second transmission unit is a double pinion type, the 2-2 planetary gear device is a single pinion type, and the 2-3 planetary gear device is a single pinion type,
The first rotating element is a sun gear of the 2-2 planetary gear device and a sun gear of the second-3 planetary gear device that are connected to each other, and the second rotating element is the 2-1 planetary gear that is connected to each other. A carrier of the device and a carrier of the 2-2 planetary gear device, wherein the third rotating element is a ring gear of the 2-2 planetary gear device and a carrier of the 2-3 planetary gear device connected to each other, The fourth rotating element is a ring gear of the 2-1 planetary gear device and the ring gear of the 2-3 planetary gear device that are connected to each other, and the fifth rotating element is a sun gear of the 2-1 planetary gear device. The multi-stage transmission according to claim 1. The 2-1 planetary gear device, the 2-2 planetary gear device, and the 2-3 planetary gear device of the second transmission unit are all single pinion types,
The first rotating element is a sun gear of the 2-1 planetary gear device, the second rotating element is a ring gear of the 2-2 planetary gear device, and the third rotating element is connected to the second 2- The carrier of the second planetary gear unit and the ring gear of the second to third planetary gear unit, wherein the fourth rotating element is connected to the carrier of the 2-1 planetary gear unit, the sun gear of the 2-2 planetary gear unit The fifth rotating element is a ring gear of the 2-1 planetary gear device and a sun gear of the 2-3 planetary gear device which are connected to each other in the carrier of the 2-3 planetary gear device. The multi-stage transmission according to claim 1. A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
Each includes a single pinion type 2-1 planetary gear device, a 2-2 planetary gear device, and a 2-3 planetary gear device, and the first rotating element is provided by the sun gear of the 2-1 planetary gear device. And the carrier of the 2-1 planetary gear device, the ring gear of the 2-2 planetary gear device, and the ring gear of the 2-3 planetary gear device are connected to each other to constitute a second rotating element, The ring gear of the 2-1 planetary gear device, the carrier of the 2-2 planetary gear device, and the carrier of the 2-3 planetary gear device are connected to each other to form a third rotating element, and the second 2- A fourth rotating element is configured by the sun gear of the three planetary gear unit, a fifth rotating element is configured by the sun gear of the 2-2 planetary gear unit, and the first rotating element is selectively selected by the first brake. rotation The second rotating element is selectively stopped by the second brake, the third rotating element is selectively stopped by the third brake, and the first rotating element engages the first clutch. The fifth rotation element is selectively connected to the second intermediate output path via a second clutch, and the first rotation element connects the third clutch to the second intermediate output path. The third rotation element is selectively connected to the first intermediate output path via a fourth clutch, and the fourth rotation element is connected to the output member. A second speed changer that outputs rotation,
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
Each includes a single pinion type 2-1 planetary gear device, a 2-2 planetary gear device, and a 2-3 planetary gear device, and the first rotating element is provided by the ring gear of the 2-1 planetary gear device. And the carrier of the 2-1 planetary gear device, the ring gear of the 2-2 planetary gear device, and the ring gear of the 2-3 planetary gear device are connected to each other to constitute a second rotating element, The carrier of the 2-2 planetary gear device and the carrier of the 2-3 planetary gear device are connected to each other to form a third rotating element, and the sun gear of the 2-3 planetary gear device forms the fourth rotating element. The sun gear of the 2-1 planetary gear device and the sun gear of the 2-2 planetary gear device are connected to each other to form a fifth rotating element, and the first rotating element is formed by the first brake. The second rotation element is selectively stopped by a second brake, the third rotation element is selectively stopped by a third brake, and the first rotation element is The fifth rotary element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotary element is selectively connected to the second intermediate output path via a second clutch. The third rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, and the fourth rotating element is A second speed changer coupled to the output member for outputting rotation;
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
Each includes a single pinion type 2-1 planetary gear device, a 2-2 planetary gear device, and a 2-3 planetary gear device, and the first rotating element is provided by the sun gear of the 2-1 planetary gear device. And the ring gear of the 2-2 planetary gear device and the ring gear of the 2-3 planetary gear device are connected to each other to form a second rotating element, and the carrier of the 2-2 planetary gear device and the carrier The carriers of the second to third planetary gear units are connected to each other to form a third rotating element, and the carrier of the second to first planetary gear unit and the sun gear of the second to third planetary gear unit are connected to each other to form a fourth. A rotating element is configured, and a ring gear of the 2-1 planetary gear device and a sun gear of the 2-2 planetary gear device are connected to each other to form a fifth rotating element, and the first rotating element is 1 blur The second rotation element is selectively stopped by a second brake, the third rotation element is selectively stopped by a third brake, and the first rotation is stopped by the key. The element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotating element is selectively connected to the second intermediate output path via a second clutch and the first rotation. The element is selectively connected to the first intermediate output path via a third clutch, and the third rotating element is selectively connected to the first intermediate output path via a fourth clutch and the fourth rotation A second transmission part connected to the output member and outputting rotation;
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
Each includes a single pinion type 2-1 planetary gear device, a 2-2 planetary gear device, and a 2-3 planetary gear device, and the first rotating element is provided by the sun gear of the 2-3 planetary gear device. The second rotating element is constituted by the ring gear of the 2-1 planetary gear device, and the carrier of the 2-1 planetary gear device and the ring gear of the 2-2 planetary gear device are connected to each other to form the second rotating element. 3 rotation elements are configured, and the carrier of the 2-2 planetary gear device and the carrier of the 2-3 planetary gear device are connected to each other to form the fourth rotation element, and the 2-1 planetary gear device A sun gear, a sun gear of the 2-2 planetary gear device, and a ring gear of the 2-3 planetary gear device are connected to each other to form a fifth rotating element, and the first rotating element is formed by the first brake. The second rotation element is selectively stopped by a second brake, the third rotation element is selectively stopped by a third brake, and the first rotation element is The fifth rotary element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotary element is selectively connected to the second intermediate output path via a second clutch. The third rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, and the fourth rotating element is A second speed changer coupled to the output member for outputting rotation;
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
A double pinion type 2-1 planetary gear device, a single pinion type 2-2 planetary gear device, and a single pinion type 2-3 planetary gear device. The sun gear and the sun gear of the 2-3 planetary gear device are connected to each other to form a first rotating element, and the carrier of the 2-1 planetary gear device and the carrier of the 2-2 planetary gear device are connected to each other. The second rotating element is configured, the ring gear of the 2-2 planetary gear device and the carrier of the 2-3 planetary gear device are connected to each other to form the third rotating element, and the 2-1 planetary gear When the ring gear of the device and the ring gear of the 2-3 planetary gear device are connected to each other to form a fourth rotating element, and the sun gear of the 2-1 planetary gear device constitutes the fifth rotating element. Furthermore, the first rotating element is selectively stopped by the first brake, the second rotating element is selectively stopped by the second brake, and the third rotating element is selected by the third brake. The first rotation element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotation element is connected to the second intermediate output path via a second clutch. The first rotating element is selectively connected to the first intermediate output path via a third clutch, and the third rotating element is connected to the first intermediate output path via a fourth clutch. A second transmission unit that is selectively coupled to the fourth rotation element and that is coupled to the output member to output rotation;
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. A first intermediate output path that transmits the rotation of the input member at a predetermined fixed speed ratio, and a speed ratio is larger than that of the first intermediate output path, and the rotation of the input member is performed more than that of the first intermediate output path. A first transmission unit comprising a second intermediate output path for transmission at low rotation;
Each includes a single pinion type 2-1 planetary gear device, a 2-2 planetary gear device, and a 2-3 planetary gear device, and the first rotating element is provided by the sun gear of the 2-1 planetary gear device. The second rotating element is constituted by the ring gear of the 2-2 planetary gear device, and the carrier of the 2-2 planetary gear device and the ring gear of the 2-3 planetary gear device are connected to each other to form the second rotating element. 3 rotation elements are configured, and the carrier of the 2-1 planetary gear device, the sun gear of the 2-2 planetary gear device, and the carrier of the 2-3 planetary gear device are connected to each other to form a fourth rotation element. The ring gear of the 2-1 planetary gear device and the sun gear of the 2-3 planetary gear device are connected to each other to form a fifth rotating element, and the first rotating element is formed by the first brake. The second rotation element is selectively stopped by a second brake, the third rotation element is selectively stopped by a third brake, and the first rotation element is The fifth rotary element is selectively connected to the second intermediate output path via a first clutch, and the fifth rotary element is selectively connected to the second intermediate output path via a second clutch. The third rotating element is selectively connected to the first intermediate output path via a third clutch, the third rotating element is selectively connected to the first intermediate output path via a fourth clutch, and the fourth rotating element is A second speed changer coupled to the output member for outputting rotation;
And a plurality of shift speeds are established by switching between engagement and disengagement states of the clutch and the brake. A first gear stage having a largest speed ratio established by engaging the second clutch and the third brake;
A second shift speed, which is established by engaging the second clutch and the second brake, and has a smaller gear ratio than the first shift speed;
A third shift speed, which is established by engaging the second clutch and the first brake, and has a gear ratio smaller than that of the second shift speed;
A fourth shift speed, which is established by engaging the first clutch and the second clutch, and has a gear ratio smaller than that of the third shift speed;
A fifth shift speed, which is established by engaging the second clutch and the third clutch, and has a smaller speed ratio than the fourth shift speed;
A sixth shift speed, which is established by engaging the second clutch and the fourth clutch, and has a smaller speed ratio than the fifth shift speed;
A seventh shift speed, which is established by engaging the third clutch and the fourth clutch, and has a gear ratio smaller than that of the sixth shift speed;
An eighth shift speed, which is established by engaging the first clutch and the fourth clutch, and has a gear ratio smaller than that of the seventh shift speed;
A ninth shift speed, which is established by engaging the fourth clutch and the first brake, and has a smaller speed ratio than the eighth shift speed;
The multi-stage transmission according to any one of claims 1 to 13, wherein a shift is performed using at least seven of the shift stages. A first shift stage in the reverse rotation direction established by engaging the first clutch and the third brake;
A second shift stage in the reverse rotation direction established by engaging the first clutch and the second brake;
The multi-stage transmission according to any one of claims 1 to 14, wherein a shift is performed using at least one of the shift stages. The first transmission unit includes a first planetary gear device, and any one of the three rotating elements of the first planetary gear device is connected to the input member to be driven to rotate, and the other one cannot be rotated. The other one is fixed as an intermediate output member so as to be transmitted to the input member while being decelerated and rotated, and the path through the intermediate output member is the second intermediate output path, and the input member The multi-stage transmission according to any one of claims 1 to 15, wherein the first intermediate output path is a path through which the rotation of the engine is directly transmitted at a gear ratio of 1.0.

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