JP4228822B2 - Planetary gear type multi-stage transmission for vehicles - Google Patents

Description

  The present invention relates to a vehicular planetary gear type multi-stage transmission provided between a prime mover and drive wheels in a vehicle such as an automobile.

  In a vehicle, a planetary gear type using a plurality of planetary gear units and engaging elements, for example, a clutch and a brake, for connecting elements constituting them to select a plurality of predetermined gear ratios or gear positions. Multi-stage transmissions are frequently used. For example, in the automatic transmission described in Patent Document 1, a multi-speed shift of seven forward speeds is achieved by using 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 planetary gear type multi-stage transmission, not only is it simple and small in size, it is possible not only to increase the number of speed stages and to increase the speed ratio width, but also to the speed ratio step to be switched. It would be desirable to be able to vary in an equal ratio or near that. The automatic transmission described in Patent Document 1 has a problem that the gear ratio step is not multistage with a setting that is convenient to use. For example, as shown in FIG. 5 of Patent Document 1, the gear ratio step between the sixth gear and the seventh gear is as small as 1.050, and the arrangement of the gear ratio steps varies widely. In addition, it is conceivable to increase the number of planetary gears in response to these problems. However, the total length of the planetary gears is increased to reduce the vehicle mountability, and the engagement elements for connecting the elements constituting the planetary gear unit. Could also increase.

  The present invention has been made against the background of the above circumstances. The object of the present invention is to provide a small vehicle capable of taking a large transmission ratio range and capable of a forward speed of 7 or more with an appropriate transmission ratio step. It is to provide a planetary gear type multi-stage transmission for use.

A first invention that achieves such an object is (a) a planetary gear type multi-stage transmission for a vehicle that is provided with a plurality of planetary gear devices and that shifts the rotation of an input rotation member and outputs it from an output rotation member. (b) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path at any one of two types of speed-up gear ratios , A first transmission that outputs the rotation of the input rotating member via at least one of the two intermediate output paths; (c) the sun gear, the carrier, and the ring gear of the third planetary gear device and the fourth planetary gear device; Four rotating elements are constructed by partially connecting to each other, and the four rotating elements are arranged from one end to the other end on a collinear chart in which the rotational speed of the four rotating elements can be represented on a straight line. Turn towards When the fifth rotating element, the sixth rotating element, the seventh rotating element, and the eighth rotating element are used, the fifth rotating element is selectively connected to the first intermediate output path via the first clutch. The sixth rotary element is selectively connected to the first intermediate output path via a second clutch, and the seventh rotary element is selectively connected to the second intermediate output path via a third clutch. The eighth rotary element is connected to the output rotating member, and is selectively connected to the second intermediate output path via a fourth clutch and is selectively connected to a non-rotating member via a third brake. (D) selectively switching between engagement and disengagement states of the clutch and brake, and selection state of the two types of speed-up gear ratios of the second intermediate output path plurality of shift stage is formed by the change of And characterized in that it is allowed. Note that the numbers that modify the planetary gear device, the clutch, and the brake are merely identification numbers and are not unique. The same applies to the following inventions.

According to a second aspect of the invention that achieves the above object, in the first aspect of the invention, the engagement and release states of the first to fourth clutches and the third brake are selectively switched and the second intermediate output path is changed. It is characterized in that at least a forward 8- speed gear stage is established by changing the selection state of the two types of speed-up gear ratios .

According to a third aspect of the invention for achieving the above object, in the second aspect of the invention, the first gear stage having the largest gear ratio is established by engaging the first clutch and the third brake, The clutch and the third brake are engaged , and the rotational state of the second intermediate output path is increased at a relatively small speed increasing speed ratio among the two speed increasing speed ratios. selected rotation state the second shift stage gear ratio is smaller than the first gear position is is established by Rukoto, the second gear position by said second clutch and said third brake are engaged A third gear stage having a smaller gear ratio is established, the second clutch and the third clutch are engaged , and the rotational state of the second intermediate output path is determined by the two types of speed-up gear ratios. Of which The fourth shift stage gear ratio than the third speed stage by Rukoto selected rotational state of being is accelerated by the speed increasing gear ratio of pairwise small side is small is is established, the first clutch and the When the second clutch is engaged, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established, and when the second clutch and the fourth clutch are engaged, the fifth shift stage is established. A sixth gear stage having a gear ratio smaller than that of the gear stage is established, the third clutch and the fourth clutch are engaged , and the rotational state of the second intermediate output path is determined by the two types of speed-up gears. of specific, the seventh shift stage gear ratio than the sixth gear position by Rukoto selected rotational state of being is accelerated by the speed increasing gear ratio of relatively small side is small is is established, the first 3 clutches and Rotation in which the fourth clutch is engaged and the rotational state of the second intermediate output path is increased at a relatively large speed increasing speed ratio among the two speed increasing speed ratios. eighth gear position gear ratio than the seventh speed stage by being selected state is small and wherein Rukoto allowed to establish.

  A fourth aspect of the invention that achieves the above object is (a) a planetary gear type multi-stage transmission for a vehicle that is provided with a plurality of planetary gear devices and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) The sun gear, the carrier, and part of the ring gear of the first planetary gear device and the second planetary gear device are connected to each other to form four rotating elements, and the four rotating elements rotate. In the collinear chart in which the speed can be expressed on a straight line, the four rotating elements are sequentially arranged from one end to the other end in the order of the first rotating element, the second rotating element, the third rotating element, and the fourth rotating element; The first rotating element is selectively connected to the non-rotating member via the first brake, the second rotating element is selectively connected to the non-rotating member via the second brake, and the third The rotating element is the input rotating unit. And a first transmission unit coupled to the first intermediate output path, the fourth rotating element coupled to the second intermediate output path, and (c) the sun gear, the carrier of the third planetary gear unit and the fourth planetary gear unit, In addition, four rotating elements are configured by connecting a part of the ring gear to each other, and at the same time, the four rotating elements are arranged at one end on a collinear diagram in which the rotational speed of the four rotating elements can be expressed on a straight line. When the fifth rotation element, the sixth rotation element, the seventh rotation element, and the eighth rotation element are sequentially formed from the first to the other end, the fifth rotation element is connected to the first intermediate output path via the first clutch. And is selectively connected to the second intermediate output path via a third clutch, and its sixth rotating element is selectively connected to the first intermediate output path via a second clutch. That first The rotating element is connected to the output rotating member, and the eighth rotating element is selectively connected to the second intermediate output path via a fourth clutch and selectively connected to the non-rotating member via a third brake. And (d) an eighth forward speed is established by selectively switching between engagement and disengagement of the clutch and brake. .

  According to a fifth aspect of the invention that achieves the above object, in the fourth aspect of the invention, the first gear stage having the largest gear ratio is established by engaging the first clutch and the third brake, By engaging the clutch, the first brake, and the third brake, a second shift stage having a smaller gear ratio than the first shift stage is established, and the second clutch and the third brake are engaged. As a result, a third gear stage having a gear ratio smaller than that of the second gear stage is established, and the second gear, the third clutch, and the first brake are engaged, whereby the third gear stage is engaged. When the fourth gear stage having a smaller gear ratio is established and the first clutch and the second clutch are engaged, the fourth gear stage is changed more than the fourth gear stage. A fifth gear having a smaller ratio is established, and a sixth gear having a smaller gear ratio than the fifth gear is established by engaging the second clutch, the fourth clutch, and the first brake. When the third clutch, the fourth clutch, and the first brake are engaged, a seventh shift stage having a speed ratio smaller than that of the sixth shift stage is established, and the third clutch, By engaging the four clutches and the second brake, an eighth speed stage having a gear ratio smaller than that of the seventh speed stage is established.

  A sixth invention that achieves the above object is a planetary gear type multi-stage transmission for a vehicle that is provided with (a) a plurality of planetary gear devices and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. And (b) a first intermediate output path for outputting the rotation of the input rotation member from the first intermediate output member, and the rotation of the input rotation member with respect to the first intermediate output path by a speed increasing device. And output a second intermediate output path and a plurality of gears, and one of the plurality of gears is connected to the drive side rotation member of the speed increasing device to increase the rotation of the input rotation member. Alternatively, a first transmission unit including a speed increasing gear device that outputs to a drive side rotating member of the speed increasing device at a constant speed, and a first intermediate output that outputs rotation of the input rotating member from a first intermediate output member. The first intermediate output of the path and the rotation of the input rotating member is increased by a speed increasing device. A second intermediate output path for speeding up the output with respect to the road; a first sun gear, a first carrier, and a first ring gear; and a first rotating member of the three rotating members. It is selectively connected to the non-rotating member via the speed increasing brake, the second rotating member is connected to the driving side rotating member of the speed increasing device, and the first rotating member and the third rotating member are selected. A first transmission unit including a first planetary gear device in which the first rotating member and the third rotating member are selectively rotated integrally by an integrated clutch connected to each other; and (c) a third The sun gear, the carrier, and the ring gear of the planetary gear device and the fourth planetary gear device are connected to each other to constitute four rotating elements, and the rotational speeds of the four rotating elements are represented on a straight line. On the nomograph When the four rotation elements of the fifth rotation element, the sixth rotation element, the seventh rotation element, and the eighth rotation element are sequentially arranged from one end to the other end, the fifth rotation element is interposed via the first clutch. Selectively coupled to the first intermediate output path and selectively coupled to the second intermediate output path via a third clutch, and the sixth rotating element thereof is coupled to the first intermediate path via the second clutch. The seventh rotary element is selectively connected to the output path, the seventh rotary element is connected to the output rotary member, and the eighth rotary element is selectively connected to the second intermediate output path via the fourth clutch and A second speed changer that is selectively connected to the non-rotating member via the three brakes, and (d) forward eight speeds by selectively switching the engagement and release states of the clutch and brake. The gear position of It is characterized by.

  According to a seventh aspect of the invention for achieving the above object, in the sixth aspect of the invention, the speed increasing gear device includes three rotating members of a first sun gear, a first carrier, and a first ring gear. The first rotating member is selectively connected to the non-rotating member via the speed increasing brake, and the second rotating member is connected to the driving side rotating member of the speed increasing device. The first planetary gear device is characterized in that the first rotating member and the third rotating member are selectively rotated integrally by an integrated clutch that selectively connects the three rotating members.

  According to an eighth aspect of the invention that achieves the above object, in the sixth or seventh aspect of the invention, the first gear stage having the largest gear ratio is established by engaging the first clutch and the third brake. When the integrated clutch, the third clutch, and the third brake are engaged, a second shift stage having a speed ratio smaller than that of the first shift stage is established, and the second clutch and the third brake are established. Is engaged to establish a third shift stage having a smaller gear ratio than the second shift stage, and the integrated clutch, the second clutch, and the third clutch are engaged to cause the third shift stage to be engaged. A fourth shift stage having a smaller speed ratio than the shift stage is established, and the first clutch and the second clutch are engaged, whereby the fourth shift stage is established. A fifth gear having a smaller gear ratio is established, and a sixth gear having a smaller gear ratio than the fifth gear is achieved by engaging the integrated clutch, the second clutch, and the fourth clutch. Is established, and the integrated clutch, the third clutch, and the fourth clutch are engaged to establish a seventh shift stage having a gear ratio smaller than that of the sixth shift stage, and the third clutch, By engaging the fourth clutch and the speed increasing brake, an eighth speed stage having a smaller gear ratio than the seventh speed stage is established.

According to a ninth aspect of the invention for achieving the above object, in any one of the first to fifth aspects, the first transmission unit and the second transmission unit are arranged in series, and the second transmission unit includes: The third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear, and is rotated by the third carrier. A double-pinion type planetary gear device having a pair of planetary gears that are supported so as to mesh with each other, and the fourth planetary gear device includes a fourth sun gear, a fourth carrier, and a fourth ring gear. The fifth rotating element is the third sun gear and the fourth sun gear, the sixth rotating element is the third ring gear and the fourth carrier, and the seventh rotation Element is its fourth ring gear, the eighth rotary element is characterized in that its third carrier.

According to a tenth aspect of the invention for achieving the above object, in the fourth aspect of the invention, the first transmission gear unit is configured such that the first planetary gear unit and the second planetary gear unit are concentrically arranged, and the first planetary gear unit is provided. The device is a single pinion type planetary gear device having a first sun gear, a first carrier, and a first ring gear, and the second planetary gear device is a single pin having a second sun gear, a second carrier, and a second ring gear. A pinion type planetary gear device, wherein the first rotating element is a first ring gear and a second sun gear, the second rotating element is a first carrier, and the third rotating element is a first sun gear and It is the second carrier, and the fourth rotating element is the second ring gear.

According to an eleventh aspect of the invention for achieving the above object, in the fourth aspect of the invention, the first transmission gear unit includes the first planetary gear unit and the second planetary gear unit that are concentrically disposed. The device is a double pinion type planetary gear device having a first sun gear, a first carrier, and a first ring gear, and having a pair of meshing planetary gears rotatably supported by the first carrier, the second planetary gear device. The gear device is a single pinion type planetary gear device including a second sun gear, a second carrier, and a second ring gear, the first rotating element is the first sun gear and the second ring gear, and the second rotating element Is the second carrier, the third rotating element is the first ring gear and the second sun gear, and the fourth rotating element is the first carrier. And wherein the door.

According to a twelfth aspect of the invention for achieving the above object, in the fourth aspect of the invention, the first transmission gear unit is configured such that the first planetary gear unit and the second planetary gear unit are disposed concentrically, and the first planetary gear unit is provided. The device is a double pinion type planetary gear device having a first sun gear, a first carrier, and a first ring gear, and having a pair of meshing planetary gears rotatably supported by the first carrier, the second planetary gear device. The gear device is a single pinion type planetary gear device provided with a second sun gear, a second carrier, and a second ring gear, the first rotating element is the first carrier and the second sun gear, and the second rotating element Is the first ring gear, the third rotating element is the first sun gear and the second carrier, and the fourth rotating element is the second ring gear. And wherein the door.

According to a thirteenth aspect of the invention for achieving the above object, in the fourth aspect of the invention, the first transmission gear unit includes the first planetary gear device and the second planetary gear device arranged concentrically, and the first planetary gear device. The device is a double pinion type planetary gear device including a first sun gear, a first carrier, and a first ring gear, and having a pair of meshing planetary gears rotatably supported by the first carrier, the second planetary gear device thereof. The gear device is a single pinion type planetary gear device including a second sun gear, a second carrier, and a second ring gear, the first rotating element is the first sun gear and the second ring gear, and the second rotating element Is the second carrier, the third rotating element is the first ring gear, and the fourth rotating element is the first carrier and the second sun gear. And features.

According to a fourteenth aspect of the present invention that achieves the above object, in the fourth aspect , the first planetary gear device and the second planetary gear device are arranged concentrically with the first planetary gear device. The device is a single pinion type planetary gear device having a first sun gear, a first carrier, and a first ring gear, and the second planetary gear device is a single pin having a second sun gear, a second carrier, and a second ring gear. A pinion type planetary gear set, wherein the first rotating element is the first sun gear and the second ring gear, the second rotating element is the second carrier, and the third rotating element is the first carrier. In addition, the fourth rotating element is a first ring gear and a second sun gear.

According to a fifteenth aspect of the invention for achieving the above object, in any one of the first to third aspects of the invention, the first axis coupled to the input rotating member and the second axis parallel to the first axis are provided. The first transmission unit includes a driving side rotating member provided on the first shaft and a driven side rotating member provided on the second shaft and rotated by the driving side rotating member. A speed increasing device is provided, and the second transmission portion is disposed on the second shaft.

  According to a sixteenth aspect of the invention for achieving the above object, in any one of the sixth to eighth aspects of the invention, a first axis connected to the input rotation member and a second axis parallel to the first axis are provided. The speed increasing device of the first transmission unit includes a driving side rotating member provided on the first shaft and a driven side provided on the second shaft and rotated by the driving side rotating member. A speed increasing gear device of the first transmission unit is disposed on the first shaft, and the second transmission unit is disposed on the second shaft.

  According to a seventeenth aspect of the invention for achieving the above object, in the fifteenth or sixteenth aspect of the invention, the second transmission portion includes the third planetary gear device and the fourth planetary gear device arranged concentrically. The third planetary gear device is a double pinion type planetary gear device including a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planet gears rotatably supported by the third carrier, The fourth planetary gear device is a single pinion type planetary gear device including a fourth sun gear, a fourth carrier, and a fourth ring gear, and the fifth rotating element is the third sun gear and the fourth sun gear, The sixth rotating element is the third ring gear and the fourth carrier, the seventh rotating element is the fourth ring gear, and the eighth rotating element is the Characterized in that it is a third carrier.

  According to an eighteenth aspect of the invention for achieving the above object, in the fifteenth or sixteenth aspect of the invention, the second transmission portion includes the third planetary gear device and the fourth planetary gear device arranged concentrically, The third planetary gear device is a single pinion type planetary gear device including a third sun gear, a third carrier, and a third ring gear, and the fourth planetary gear device includes a fourth sun gear, a fourth carrier, and a fourth ring gear. Wherein the fifth rotating element is the third sun gear and the fourth sun gear, the sixth rotating element is the fourth carrier, and the seventh rotating element is the first sun gear. A third carrier and a fourth ring gear, wherein the eighth rotating element is the third ring gear.

  According to a nineteenth aspect of the present invention that achieves the above object, in the fifteenth or sixteenth aspect of the present invention, the second transmission portion includes the third planetary gear device and the fourth planetary gear device arranged concentrically. The third planetary gear device is a double pinion type planetary gear device including a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planet gears rotatably supported by the third carrier, The fourth planetary gear device is a single pinion type planetary gear device including a fourth sun gear, a fourth carrier, and a fourth ring gear, and the fifth rotating element is the third carrier and the fourth sun gear, The sixth rotating element is the third ring gear and the fourth carrier, the seventh rotating element is the fourth ring gear, and the eighth rotating element is the Characterized in that 3 is the sun gear.

  According to a twentieth aspect of the invention for achieving the above object, in the fifteenth or sixteenth aspect of the invention, the second transmission unit includes the third planetary gear device and the fourth planetary gear device arranged concentrically. The third planetary gear device is a double pinion type planetary gear device including a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planet gears rotatably supported by the third carrier, The fourth planetary gear device is a single pinion type planetary gear device including a fourth sun gear, a fourth carrier, and a fourth ring gear, the fifth rotating element is the fourth sun gear, and the sixth rotating element is The third carrier and the fourth carrier, the seventh rotating element is the third ring gear and the fourth ring gear, and the eighth rotating element is the Characterized in that 3 is the sun gear.

  According to a twenty-first aspect of the invention that achieves the above object, in the twentieth aspect, the third carrier, the fourth carrier, the third ring gear, and the fourth ring gear are each composed of a common member, and The planetary gear of the four planetary gear unit also serves as any one of a pair of planetary gears that mesh with each other of the third planetary gear unit.

  According to a twenty-second aspect of the invention for achieving the above object, in the fifteenth or sixteenth aspect of the invention, the second transmission portion includes the third planetary gear device and the fourth planetary gear device arranged concentrically. The third planetary gear device is a double pinion type planetary gear device including a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planet gears rotatably supported by the third carrier, The fourth planetary gear device is a single pinion type planetary gear device including a fourth sun gear, a fourth carrier, and a fourth ring gear, and the fifth rotating element is the third carrier and the fourth sun gear, The sixth rotating element is the third ring gear, the seventh rotating element is the fourth carrier, and the eighth rotating element is the third sun gear and the fourth ring. Characterized in that it is a Ya.

In addition, in a twenty-third aspect of the present invention that achieves the above object, in any one of the first to twenty-second aspects, the sixth rotating element is selectively connected to a non-rotating member via a fourth brake. The reverse speed is established by engaging the fourth brake and the first clutch.

A twenty-fourth aspect of the invention that achieves the above object is a planetary gear type multi-stage transmission for a vehicle that is provided with (a) a plurality of planetary gear devices and that changes the speed of rotation of an input rotary member and outputs it from an output rotary member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear. And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch. The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier is connected to the second clutch via the fourth clutch. A second transmission part that is selectively connected to the intermediate output path and selectively connected to the non-rotating member via a third brake, (d) engagement of the clutch and brake, a plurality of gear stages is is established by switching the released state selectively, (e) said first transmission portion includes a first sun gear, a single-pinion type having a first carrier, and a first ring gear 1 and the planetary gear unit, a second sun gear, a second carrier, and a second planetary gear set of a single pinion type having a second ring gear, the first ring gear and a second sun gear the first brake (f) The first carrier is selectively connected to the non-rotating member via the second brake, and the first sun gear and the second carrier are connected to the input rotating member and the first rotating member. The second ring gear is connected to the intermediate output path, and the second ring gear is connected to the second intermediate output path.

According to a twenty-fifth aspect of the present invention , the vehicle planetary gear type multi-stage transmission includes a plurality of planetary gear devices, and shifts the rotation of the input rotation member and outputs it from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear. And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch. The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier is connected to the second clutch via the fourth clutch. A second transmission part that is selectively connected to the intermediate output path and selectively connected to the non-rotating member via a third brake, (d) engagement of the clutch and brake, a plurality of gear stages is is established by switching the released state selectively, (e) said first transmission portion includes a first sun gear, comprising a first carrier, and a first ring gear, on the first carrier A double pinion type first planetary gear device having a pair of meshing planetary gears supported in a rotatable manner, and a single pinion type second planetary gear device having a second sun gear, a second carrier, and a second ring gear. (F) the first sun gear and the second ring gear are selectively connected to the non-rotating member via the first brake, and the second carrier is selectively connected to the non-rotating member via the second brake. The first ring gear and the second sun gear are connected to the input rotating member and the first intermediate output path, and the first carrier is connected to the second intermediate output path.

According to a twenty-sixth aspect of the present invention , the vehicle planetary gear type multi-stage transmission includes a plurality of planetary gear devices, and shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear. And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch. The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier is connected to the second clutch via the fourth clutch. A second transmission part that is selectively connected to the intermediate output path and selectively connected to the non-rotating member via a third brake, (d) engagement of the clutch and brake, a plurality of gear stages is is established by switching the released state selectively, (e) said first transmission portion includes a first sun gear, comprising a first carrier, and a first ring gear, on the first carrier And a double pinion type first planetary gear device having a pair of meshing planet gears supported rotatably and a single pinion type second planetary gear device having a second sun gear, a second carrier, and a second ring gear. (F) the first carrier and the second sun gear are selectively connected to the non-rotating member via the first brake, and the first ring gear is selectively connected to the non-rotating member via the second brake. The first sun gear and the second carrier are connected to the input rotating member and the first intermediate output path, and the second ring gear is connected to the second intermediate output path.

According to a twenty-seventh aspect of the present invention , the vehicle planetary gear type multi-stage transmission includes a plurality of planetary gear devices and shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear. And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch. The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier is connected to the second clutch via the fourth clutch. A second transmission part that is selectively connected to the intermediate output path and selectively connected to the non-rotating member via a third brake, (d) engagement of the clutch and brake, a plurality of gear stages is is established by switching the released state selectively, (e) said first transmission portion includes a first sun gear, comprising a first carrier, and a first ring gear, on the first carrier And a double pinion type first planetary gear device having a pair of meshing planet gears supported rotatably and a single pinion type second planetary gear device having a second sun gear, a second carrier, and a second ring gear. (F) the first sun gear and the second ring gear are selectively connected to the non-rotating member via the first brake, and the second carrier is selectively connected to the non-rotating member via the second brake. The first ring gear is connected to the input rotating member and the first intermediate output path, and the first carrier and the second sun gear are connected to the second intermediate output path.

According to a twenty-eighth aspect of the present invention for achieving the above object, there is provided a planetary gear type multi-stage transmission for a vehicle comprising : (a) a plurality of planetary gear devices, wherein the rotation of the input rotating member is shifted and output from the output rotating member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear. And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch. The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier is connected to the second clutch via the fourth clutch. A second transmission part that is selectively connected to the intermediate output path and selectively connected to the non-rotating member via a third brake, (d) engagement of the clutch and brake, a plurality of gear stages is is established by switching the released state selectively, (e) said first transmission portion includes a first sun gear, a single-pinion type having a first carrier, and a first ring gear 1 and the planetary gear unit, a second sun gear, a second carrier, and a second planetary gear set of a single pinion type having a second ring gear, the first sun gear and a second ring gear the first brake (f) The second carrier is selectively connected to the non-rotating member via the second brake, and the first carrier is connected to the input rotating member and the first intermediate output path. The first ring gear and the second sun gear are connected to the second intermediate output path.

In addition, the 29 present invention to achieve the object, selectively in any one of the twenty-fourth aspect to the 28th invention, the first clutch to the fourth clutch and the first brake to engage the third brake, the release state By switching to, at least a forward seventh speed is established.

In addition, the 30 present invention to achieve the object is any one of the twenty-fourth aspect to the 29th invention, the first gear of the highest speed ratio by the first clutch and the third brake are engaged Is established, and the second clutch having a smaller gear ratio than the first gear is established by engaging the third clutch, the first brake, and the third brake, and the second clutch When the third brake is engaged, a third gear having a smaller gear ratio than the second gear is established, and the second clutch, the third clutch, and the first brake are engaged. As a result, a fourth shift stage having a smaller gear ratio than the third shift stage is established, and the first clutch and the second clutch are engaged. Therefore, the fifth shift stage having a smaller gear ratio than the fourth shift stage is established, and the second clutch, the fourth clutch, and the first brake are engaged, thereby shifting the speed compared to the fifth shift stage. A sixth gear with a small ratio is established, and a seventh gear with a smaller gear ratio than the sixth gear is established by engaging the third clutch, the fourth clutch, and the first brake. And the third clutch, the fourth clutch, and the second brake are engaged, whereby the eighth speed stage having a smaller gear ratio than the seventh speed stage is established.

In a thirty-first aspect of the present invention that achieves the above object, in any one of the twenty-fourth to thirtieth aspects, the third ring gear and the fourth carrier are selectively connected to a non-rotating member via a fourth brake. The reverse gear is established by engaging the fourth brake and the first clutch.

A thirty-second invention for achieving the above object is (a) a planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) a first shaft connected to the input rotating member; (c) a second shaft parallel to the first axis; and (d-1) rotating the input rotating member to a first intermediate output member. A first intermediate output path for output from (d-2) a driving side rotating member provided on the first axis, and a driven side provided on the second axis and rotated by the driving side rotating member A speed increasing device that has a rotating member and accelerates the rotation of the input rotating member; and (d-3) a second intermediate output that is accelerated and outputted to the first intermediate output path by the speed increasing device. (D-4) having a plurality of gears, and one of the plurality of gears is connected to the driving side rotation member of the speed increasing device, and the input rotation A first speed changer comprising a speed increasing gear device that increases the rotation of the material at a constant speed or outputs it to the drive side rotating member of the speed increasing device; (e) a third sun gear, a third carrier, And a third planetary gear device of a double pinion type having a pair of meshing planetary gears rotatably supported by the third carrier, a fourth sun gear, a fourth carrier, and a fourth ring gear. A single pinion type fourth planetary gear device, the third sun gear and the fourth sun gear being selectively connected to the first intermediate output path via the first clutch and via the third clutch. The third ring gear and the fourth carrier are selectively connected to the second intermediate output path, and the fourth ring gear is selectively connected to the first intermediate output path via a second clutch. Is coupled to the output rotating member, and the third carrier is selectively coupled to the second intermediate output path via a fourth clutch and is selectively coupled to the non-rotating member via a third brake. And (f) a plurality of shift speeds are established by selectively switching between engagement and disengagement states of the clutch and the brake.

Further, 33rd invention for achieving the above object, in the 32 invention, the speed increasing gear includes a first sun gear, a first carrier, provided with three rotational members of the first ring gear, among the three rotating members The first rotating member is selectively connected to the non-rotating member via the speed increasing brake, and the second rotating member is connected to the driving side rotating member of the speed increasing device. The first planetary gear device is characterized in that the first rotating member and the third rotating member are selectively rotated integrally by an integrated clutch that selectively connects the three rotating members.

According to a thirty-fourth aspect of the present invention that achieves the above object, in the thirty-second or thirty- third aspect, the third ring gear and the fourth carrier are selectively connected to a non-rotating member via a fourth brake. A reverse speed is established by engaging the fourth brake and the first clutch.

A thirty-fifth aspect of the present invention that achieves the above object is a planetary gear type multi-stage transmission for a vehicle that is provided with (a) a plurality of planetary gear devices and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission unit that outputs through at least one of the intermediate output paths; (c) a single pinion type third planetary gear device including a third sun gear, a third carrier, and a third ring gear; A single pinion type fourth planetary gear device having a sun gear, a fourth carrier, and a fourth ring gear, wherein the third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch. Linked to And the fourth carrier is selectively connected to the second intermediate output path via a third clutch, the fourth carrier is selectively connected to the first intermediate output path via a second clutch, and the third carrier and The fourth ring gear is connected to the output rotating member, and the third ring gear is selectively connected to the second intermediate output path via a fourth clutch and selectively connected to the non-rotating member via a third brake. And (d) a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake , and (e) the input rotation A first shaft coupled to the member and a second shaft parallel to the first shaft; (f) the first transmission unit outputs a rotation of the input rotation member from the first intermediate output member; 1 intermediate output path and its first axis A speed increasing device that has a driving side rotating member provided and a driven side rotating member that is provided on the second shaft and is rotated by the driving side rotating member, and that accelerates the rotation of the input rotating member; (g) a second intermediate output path that outputs an increased speed to the first intermediate output path by the speed increasing device; and (g) a plurality of gears, and one of the plurality of gears is It is connected to the driving side rotating member of the speed increasing system, that you have a speed increasing gear that outputs a driving-side rotating member of the speed increasing system at by accelerating the rotation of the input rotary member or constant velocity Features.

Also, the 36th invention for achieving the above object, in the 35th invention, wherein the fourth carrier is selectively connected to a non-rotating member via a fourth brake, the fourth brake and the first clutch Is established, the reverse gear is established.

A thirty-seventh aspect of the present invention that achieves the above object is a planetary gear type multi-stage transmission for a vehicle that is provided with (a) a plurality of planetary gear devices and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear, (d) the third Carrier And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch, and the third ring gear and The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotation member, and the third sun gear is connected to the first intermediate output path via the fourth clutch. And (e) engagement of the clutch and the brake, wherein the second transmission is selectively connected to the intermediate output path and selectively connected to the non-rotating member via the third brake. A plurality of shift stages are established by selectively switching the disengaged state , and (f) a first shaft coupled to the input rotation member, and a second shaft parallel to the first shaft, g) The first transmission unit is A first intermediate output path for outputting the rotation of the input rotation member from the first intermediate output member, a drive side rotation member provided on the first axis, and a drive side rotation member provided on the second axis And a speed increasing device for increasing the rotation of the input rotating member, and (h) increasing the speed with respect to the first intermediate output path by the speed increasing device for output. A second intermediate output path, and (i) a plurality of gears, one of the plurality of gears being connected to the drive side rotation member of the speed increasing device, and increasing the rotation of the input rotation member or at a constant speed, it characterized that you have a speed increasing gear that outputs a driving-side rotating member of the speed increasing system.

According to a thirty- eighth aspect of the present invention that achieves the above object, in the thirty-seventh aspect , the third ring gear and the fourth carrier are selectively connected to a non-rotating member via a fourth brake. The reverse gear is established by engaging the first clutch.

A thirty-ninth aspect of the present invention that achieves the above object is a planetary gear type multi-stage transmission for a vehicle, which comprises (a) a plurality of planetary gear devices, and shifts the rotation of the input rotation member and outputs it from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear, the fourth sun gear being The first carrier is selectively connected to the first intermediate output path via one clutch and is selectively connected to the second intermediate output path via a third clutch. The third carrier and the fourth carrier are second A third ring gear and a fourth ring gear are selectively connected to the output rotating member via a clutch, and the third sun gear is connected to the second intermediate output via a fourth clutch. A second transmission portion selectively connected to the path and selectively connected to the non-rotating member via a third brake, and (d) engaged and released states of the clutch and the brake (E) a first shaft connected to the input rotation member, and a second shaft parallel to the first shaft, and (f) the The first transmission unit is A first intermediate output path for outputting the rotation of the rotation member from the first intermediate output member, a drive side rotation member provided on the first axis, and a rotation by the drive side rotation member provided on the second axis A speed increasing device having a driven side rotating member that is driven, and speeding up the rotation of the input rotating member; and (g) a speed increasing device that outputs the speed to the first intermediate output path by the speed increasing device. 2 intermediate output path, and (h) having a plurality of gears, one of the plurality of gears being connected to the drive side rotation member of the speed increasing device, increasing the rotation of the input rotation member or the like It has a speed increasing gear that outputs a driving-side rotating member of the speed increasing system at speed and said Rukoto.

According to a 40th aspect of the invention for achieving the above object, in the 39th aspect of the invention, the third carrier, the fourth carrier, the third ring gear, and the fourth ring gear are each constituted by a common member, and The planetary gear of the four planetary gear unit also serves as any one of a pair of planetary gears that mesh with each other of the third planetary gear unit .

According to a 41st aspect of the present invention for achieving the above object, in the 39th to 40th aspects of the present invention, the third carrier and the fourth carrier are selectively connected to a non-rotating member via a fourth brake. A reverse speed is established by engaging the fourth brake and the first clutch.

According to a forty-second aspect of the present invention, the vehicle planetary gear type multi-stage transmission includes a plurality of planetary gear devices, and shifts the rotation of the input rotation member and outputs the rotation from the output rotation member. (B) two intermediate output paths including a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is A first transmission that outputs through at least one of the intermediate output paths; and (c) a third sun gear, a third carrier, and a third ring gear, which mesh with each other and are rotatably supported by the third carrier. A double pinion type third planetary gear device having a pair of planetary gears, and a single pinion type fourth planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear. And the fourth sun gear is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch, and the third ring gear is The second carrier is selectively connected to the first intermediate output path via two clutches, the fourth carrier is connected to the output rotating member, and the third sun gear and the fourth ring gear are connected to the second intermediate output path via the fourth clutch. And (d) engagement and release of the clutch and brake, the second transmission part being selectively connected to the output path and selectively connected to the non-rotating member via the third brake. (E) a first shaft coupled to the input rotation member, and a second shaft parallel to the first shaft; and (f) The first transmission unit is configured to input the input circuit. The first intermediate output path for outputting the rotation of the member from the first intermediate output member, the driving side rotating member provided on the first shaft, and the driving side rotating member provided on the second shaft. A speed increasing device for increasing the rotation of the input rotating member, and (g) a second speed increasing device for output to the first intermediate output path by the speed increasing device. An intermediate output path and (h) a plurality of gears, one of the plurality of gears being connected to the drive side rotation member of the speed increasing device, increasing the rotation of the input rotation member or constant speed at characterized that you have a speed increasing gear that outputs a driving-side rotating member of the speed increasing system.

Further, 43rd invention for achieving the above object, in the 42 invention, the third ring gear is selectively connected to a non-rotating member via a fourth brake, the fourth brake and the first clutch Is established, the reverse gear is established.

According to a 44th aspect of the invention for achieving the above object, in any one of the 35th to 43rd aspects of the invention, the speed increasing gear device includes three rotating members of a first sun gear, a first carrier, and a first ring gear. The first rotating member of the three rotating members is selectively connected to the non-rotating member via the speed increasing brake, and the second rotating member is connected to the driving side rotating member of the speed increasing device, The first planetary gear device in which the first rotating member and the third rotating member are selectively rotated integrally by an integrated clutch that selectively connects the first rotating member and the third rotating member. It is characterized by being.

According to a 45th aspect of the invention for attaining the above object, in any one of the 32nd to 44th aspects of the invention, at least a seventh forward speed can be achieved by selectively switching the engagement and release states of the clutch and brake. It is characterized by being established.

According to a forty- sixth aspect of the present invention for achieving the above object, in the forty- fifth aspect, the first shift stage having the largest speed ratio is established by engaging the first clutch and the third brake, and the integration is performed. By engaging the clutch, the third clutch, and the third brake, a second shift stage having a smaller speed ratio than the first shift stage is established, and the second clutch and the third brake are engaged. As a result, a third gear stage having a smaller gear ratio than the second gear stage is established, and the integrated clutch, the second clutch, and the third clutch are engaged with each other to engage the third gear stage. A fourth shift stage having a small gear ratio is established, and the first clutch and the second clutch are engaged, so that the fourth shift stage changes more than the fourth shift stage. A fifth gear having a smaller ratio is established, and the sixth gear having a smaller gear ratio than the fifth gear is established by engaging the integrated clutch, the second clutch, and the fourth clutch. When the integrated clutch, the third clutch, and the fourth clutch are engaged, a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established, and the third clutch, the fourth clutch The eighth speed stage having a gear ratio smaller than that of the seventh speed stage is established by engaging the speed increasing brake.

According to a 47th aspect of the present invention that achieves the above object, in any one of the first to 46th aspects, the output of the engine is input to the input rotation member via a fluid transmission device. And

According to the first to 47th aspects of the present invention, the first speed change unit, the third planetary gear device, and the fourth planetary gear device can provide at least the seventh forward speed with a large speed ratio range and an appropriate speed ratio step. Or, a small-sized planetary gear type multi-stage transmission for a vehicle capable of eight forward speeds can be obtained.

Further, the fifteenth aspect to the twenty-second invention, and according to the 32 invention to any one of the invention of the 46th invention, for the axial dimension shorter vehicle planetary gear type multi-speed transmission is obtained.

According to the 23rd, 31st , 33rd , 36th , 38th , 41st and 43rd inventions, in addition to the forward speed of 7 or more speeds or the forward speed of 8th speed, the reverse drive One shift gear is obtained.

According to the twenty-first or forty-first invention, since the so-called Ravigneaux type planetary gear train is used, the number of parts and the shaft length can be further reduced.

According to the forty- seventh aspect, a compact automatic transmission can be designed.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a skeleton diagram illustrating a configuration of a vehicular planetary gear type multi-stage transmission (hereinafter referred to as a transmission) 10 suitable as an automatic transmission for a vehicle. In FIG. 1, a transmission 10 is connected to a torque converter 14 with a lock-up clutch 13 as a fluid transmission device that is sequentially disposed on a common axis in a transmission case 12 attached to a vehicle body, and is connected to the torque converter 14. The input shaft 16, the first planetary gear device 18 and the second planetary gear device 20 are mainly configured by the first transmission unit 36, the third planetary gear device 22 and the fourth planetary gear device 24. The second transmission unit 38 and the output shaft 26 are concentrically provided. The transmission 10 is preferably used as an FR automatic transmission that is installed vertically in a vehicle, and is provided between the engine 8 and drive wheels (not shown), and transmits the output of the engine 8 to the drive wheels. . In this embodiment, the input shaft 16 and the output shaft 26 correspond to an input rotating member and an output rotating member, and the transmission case 12 corresponds to a non-rotating member. The torque converter 14 is connected to the crankshaft 9 of the engine 8, and the output shaft 26 rotationally drives the left and right drive wheels through, for example, a differential gear device (not shown). Since the transmission 10 is configured symmetrically with respect to its axis, the lower side is omitted in the skeleton diagram of FIG.

The first planetary gear unit 18 and the second planetary gear unit 20 of the first transmission unit 36 are each a single pinion type planetary gear unit, and from the torque converter 14 to the first planetary gear unit 18 and the second planetary gear unit. They are arranged in the order of 20. The first planetary gear unit 18 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear S1 via the first planetary gear P1. And has a predetermined gear ratio ρ ₁ (= the number of teeth Z _{S1 of} the first sun gear _S1 / the number of teeth Z _R1 of the first ring gear _R1 ), for example, about “0.406”. ing. The second planetary gear unit 20 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. And has a predetermined gear ratio ρ ₂ of about “0.511” (= number of teeth Z _S2 of second sun gear _S2 / number of teeth Z R2 of second ring gear _R2 ), for example. ing.

  In the first transmission unit 36, the first sun gear S1 is connected to the input shaft 16 and a first intermediate output path (first intermediate output member) M1 disposed concentrically with the input shaft 16, and the first carrier CA1. Is selectively connected to the transmission case 12 via the second brake B2, and the first ring gear R1 is selectively connected to the transmission case 12 via the first brake B1, and is integrated with the second sun gear S2. The second carrier CA2 is connected to the input shaft 16 and the first intermediate output path M1, and the second ring gear R2 is connected to the second intermediate output path (second intermediate output member) M2. In the first transmission unit 36 configured as described above, the rotation of the input shaft 16 is output to the second transmission unit 38 from at least one of the first intermediate output path M1 and the second intermediate output path M2. When the rotation of the input shaft 16 is output from the second intermediate output path M2, it is rotated at an increased speed with respect to the first intermediate output path M1 and output. In the present embodiment, since the first intermediate output path M1 is connected to the input shaft 16, the first intermediate output path M1 is rotated at the same rotational speed as the input shaft 16, but the first intermediate output path M1 is rotated. The rotational speed of the output path M1 does not need to be the same as the rotational speed of the input shaft 16.

The third planetary gear device 22 and the fourth planetary gear device 24 constituting the second transmission unit 38 are double pinion type and single pinion type planetary gear devices, respectively. That is, the third planetary gear unit 22 includes a third sun gear S3, a plurality of pairs of third planetary gears P3 that mesh with each other, a third carrier CA3 that supports the third planetary gear P3 so as to be capable of rotating and revolving, and a third planetary gear P3. Is provided with a third ring gear R3 meshing with the third sun gear S3, for example, a predetermined gear ratio ρ ₃ of about “0.452” (= the number of teeth of the third sun gear S3 Z _S3 / the teeth of the third ring gear R3 has a number _{Z R3),} the fourth planetary gear set 24 includes a fourth sun gear S4, a fourth planet gear P4, a fourth carrier CA4 rotatably and revolvably supports the fourth planetary gear P4, a fourth and a fourth ring gear R4 meshing with the fourth sun gear S4 via the planetary gear P4, for example, "0.500" approximately of a predetermined gear ratio [rho ₄ (= number of teeth _{Z S4} / a fourth sun gear S4 It has a number of teeth _{Z R4} ring gear R4).

  In the second transmission unit 38, the third sun gear S3 and the fourth sun gear S4 are integrally connected to be selectively connected to the first intermediate output path M1 via the first clutch C1 and the third clutch. The third carrier CA3 is selectively connected to the second intermediate output path M2 via the fourth clutch C4 and the third brake B3 is connected to the second intermediate output path M2 via the C3. The third ring gear R3 and the fourth carrier CA4 are integrally connected to each other and selectively connected to the first intermediate output path M1 via the second clutch C2. The fourth ring gear R4 is connected to the output shaft 26 by being selectively connected to the transmission case 12 via the fourth brake B4.

  The clutches C1 to C4 and the brakes B1 to B4 are hydraulic friction engagement devices often used in conventional automatic transmissions for vehicles, and a plurality of friction plates stacked on each other are pressed by a hydraulic actuator. The wet-type multi-plate type, or one or two bands wound around the outer peripheral surface of the rotating drum are composed of a band brake that is tightened by a hydraulic actuator. For selective connection.

In the transmission 10 configured as described above, for example, as shown in the engagement operation table of FIG. 2, two to three selected from the clutches C1 to C4 and the brakes B1 to B4 are simultaneously engaged. By being moved, any one of the first speed gear stage (first gear stage) to the eighth speed gear stage (eighth gear stage) or the reverse gear stage (reverse gear stage) is selectively established. A gear ratio γ (= input shaft rotational speed N _IN / output shaft rotational speed N _OUT ) that changes in an equal ratio is obtained for each gear stage.

That is, as shown in FIG. 2, the engagement of the first clutch C1 and the third brake B3 causes the third carrier CA3 and the transmission case between the first intermediate output path M1 and the third sun gear S3 and the fourth sun gear S4. by between 12 are respectively connected, first speed ratio [gamma ₁ is the maximum value, for example, "3.842" is established. Further, due to the engagement of the third clutch C3, the first brake B1 and the third brake B3, the first ring gear R1 and the second sun gear S2 between the second intermediate output path M2 and the third sun gear S3 and the fourth sun gear S4. and between the transmission case 12, by between a third carrier CA3 and the transmission case 12 are respectively connected, the speed ratio gamma ₂ is a small value, for example, "2.543" degree than first gear The second gear is established. Further, the engagement of the second clutch C2 and the third brake B3 connects the first intermediate output path M1 and the fourth carrier CA4 and the third ring gear R3, and the third carrier CA3 and the transmission case 12, respectively. Thus, the _third speed gear stage in which the speed ratio γ3 is smaller than the second speed gear stage, for example, about “1.737” is established. Further, due to the engagement of the second clutch C2, the third clutch C3, and the first brake B1, the second intermediate output path M2 and the third ring gear R3 are connected between the first intermediate output path M1 and the fourth carrier CA4 and the third ring gear R3. between the sun gear S3 and fourth sun gear S4, by between the first ring gear R1 and second sun gear S2 and the transmission case 12 are respectively connected, smaller speed ratio gamma ₄ than the third speed position e.g. A fourth gear that is about "1.218" is established. Further, due to the engagement of the first clutch C1 and the second clutch C2, between the first intermediate output path M1 and the third sun gear S3 and the fourth sun gear S4, the first intermediate output path M1 and the fourth carrier CA4 and the third By connecting the ring gear R3 to each other, the _fifth speed gear stage in which the speed ratio γ5 is smaller than the fourth speed gear stage, for example, about “1.000” is established. Further, due to the engagement of the second clutch C2, the fourth clutch C4, and the first brake B1, the second intermediate output path M2 and the third ring gear R3 are connected between the first intermediate output path M1 and the fourth carrier CA4 and the third ring gear R3. between the carrier CA3, by between the first ring gear R1 and second sun gear S2 and the transmission case 12 are respectively connected, smaller speed ratio gamma ₆ is than the fifth gear, for example, "0.822" The sixth gear is established. Further, due to the engagement of the third clutch C3, the fourth clutch C4 and the first brake B1, the second intermediate output path M2 and the third sun gear S4 are connected between the second intermediate output path M2 and the third sun gear S3 and the fourth sun gear S4. between the carrier CA3, by between the first ring gear R1 and second sun gear S2 and the transmission case 12 are respectively connected, smaller speed ratio gamma ₇ is than the sixth gear, for example, "0.622" The seventh gear is established. Further, due to the engagement of the third clutch C3, the fourth clutch C4, and the second brake B2, the second intermediate output path M2 and the third sun gear S4 are connected between the second intermediate output path M2 and the third sun gear S3 and the fourth sun gear S4. between the carrier CA3, by between the first carrier CA1 and the transmission case 12 are respectively connected, the eighth speed gear ratio gamma ₈ is "0.582" smaller for example than the seventh-speed position A gear stage is established. In the first speed gear stage, the third speed gear stage, and the fifth speed gear stage, the first brake B1 may be further engaged.

Further, due to the engagement of the first clutch C1 and the fourth brake B4, between the first intermediate output path M1 and the third sun gear S3 and the fourth sun gear S4, the third ring gear R3 and the fourth carrier CA4, and the transmission case 12, Are connected to each other to establish a reverse gear stage in which the gear ratio γ _R is a value between the first speed gear stage and the second speed gear stage, for example, “2.875”. The gear ratio [rho ₁ of the first planetary gear unit _18, the gear ratio [rho ₂ of the second planetary gear _20, the gear ratio [rho ₃ of the third planetary gear unit _22, the gear ratio [rho ₄ of the fourth planetary gear set 24, It is set so as to obtain the gear ratio as described above.

In the transmission 10, the ratio (= γ ₁ / γ ₂ ) between the speed ratio γ ₁ of the first speed gear stage and the speed ratio γ ₂ of the second speed gear stage is set to “1.511”. The ratio (= γ ₂ / γ ₃ ) between the speed ratio γ ₂ of the gear stage and the speed ratio γ ₃ of the third speed gear stage is set to “1.464”, and the speed ratio γ ₃ of the third speed gear stage and the the ratio of the speed ratio gamma ₄ of the fourth gear (= γ _{3 /} γ ₄₎ is set to "1.426", the gear ratio of the gear ratio of the fourth gear gamma ₄ and the fifth gear gamma ₅ is the ratio (= γ ₄ / γ ₅₎ is "1.218" with the ratio of the speed ratio gamma ₆ the speed ratio gamma ₅ in fifth gear sixth gear stage (= gamma ₅ / gamma ₆ ) is set to “1.217”, and the ratio (= γ ₆ / γ ₇ ) between the speed ratio γ ₆ of the sixth speed gear and the speed ratio γ ₇ of the seventh speed gear is set to “1.242”. It is the ratio of the speed ratio gamma ₈ and the gear ratio gamma ₇ of the seventh-speed position eighth gear ( γ _{7 /} γ ₈₎ is set to "1.137", it is varied as the speed ratio gamma gradually decreases in a narrow range a substantially equal ratio. In the above transmission 10, the speed ratio gamma ₁ and which is the ratio gear ratio range of the gear ratio gamma ₈ of eighth gear (= γ _{1 /} γ ₈₎ is relatively large value of the first gear That is, it is set to “6.604”.

FIG. 3 is a collinear diagram that can represent, on a straight line, the relative relationship between the rotational speeds of the rotating elements that are connected in different gear stages in the transmission 10. The collinear chart of FIG. 3 is a two-dimensional coordinate system showing the relationship of the gear ratio ρ of each planetary gear unit 18, 20, 22, 24 in the horizontal axis direction and the relative rotational speed in the vertical axis direction. The horizontal line X1 on the lowermost side of the horizontal line X1 indicates the rotational speed zero, the horizontal line X2 on the upper side thereof indicates the rotational speed “1.0”, that is, the rotational speed of the first intermediate output path M1, and the horizontal line XG1 on the upper side thereof. XG2 is a predetermined rotational speed “N _G1 ” “N _G2 ” determined based on the gear ratios ρ ₁ , ρ ₂ of the first planetary gear device 18 and the second planetary gear device 20, and these rotational speeds N _G1 , N _G2 is rotating at an increased speed with respect to the first intermediate output path M1. The vertical lines Y1 to Y8 represent the first rotation element RE1 to the eighth rotation element RE8 in order from the left, and the first rotation element RE1 is connected to the first ring gear R1 and the second sun gear S2. The second rotating element RE2 is the first carrier CA1, the third rotating element RE3 is the first sun gear S1 and the second carrier CA2 connected to each other, and the fourth rotating element RE4 is the second ring gear R2. The fifth rotation element RE5 is a third sun gear S3 and a fourth sun gear S4 that are connected to each other, and the sixth rotation element RE6 is a third ring gear R3 and a fourth carrier CA4 that are connected to each other. The rotating element RE7 is the fourth ring gear R4, and the eighth rotating element RE8 is the third carrier CA3. The intervals between the vertical lines Y1 to Y4 are respectively determined according to the gear ratios ρ ₁ and ρ ₂ of the first planetary gear device 18 and the second planetary gear device 20, and the intervals between the vertical lines Y5 to Y8 are third. The planetary gear device 22 and the fourth planetary gear device 24 are respectively determined according to the gear ratios ρ ₃ and ρ ₄ , and the vertical axis interval in the nomograph is “1” between the sun gear and the carrier. And the ring gear are set to be ρ.

  If expressed using the collinear diagram, the transmission 10 of the present embodiment is configured such that the first transmission element RE1 (R1, S2) is transmitted through the first brake B1 in the first transmission unit 36. The second rotating element RE2 (CA1) is selectively connected to the transmission case 12 via the second brake B2, and the third rotating element RE3 (S1, CA2) is connected to the input shaft 16 and The fourth rotation element RE4 (R2) is connected to the first intermediate output path M1, and the fourth rotation element RE4 (R2) is connected to the second intermediate output path M2. In the second transmission unit 38, the fifth rotation element RE5 (S3) is connected. , S4) are selectively coupled to the first intermediate output path M1 via the first clutch C1 and to the second ring gear R2 (second intermediate output path M2) via the third clutch C3. The sixth rotating element RE6 (R3, CA4) is selectively connected to the first intermediate output path M1 via the second clutch C2, and the transmission case 12 via the fourth brake B4. The seventh rotating element RE7 (R4) is connected to an output shaft (output rotating member) 26, and the eighth rotating element RE8 (CA3) is connected to the second ring gear R2 via the fourth clutch C4. It is configured to be selectively connected to the (second intermediate output path M2) and selectively connected to the transmission case 12 via the third brake B3.

  Each speed gear stage will be described with reference to the collinear diagram of FIG. In the first speed gear stage, the fifth rotation element RE5 is connected to the first intermediate output path M1 by the engagement of the first clutch C1 and is set to the rotation speed “1”, and the eighth rotation element RE8 is connected to the third brake B3. Since it is connected to the transmission case 12 by engagement and the rotational speed is set to “0”, a straight line connecting the intersection of the vertical line Y5 and the horizontal line X2 and the intersection of the vertical line Y8 and the horizontal line X1 intersects the vertical line Y7. The rotational speed of the output shaft 26 is indicated by the point (1st).

At the second speed gear stage, in the first transmission unit 36, the first rotational element RE1 is set to the rotational speed “0” by the engagement of the first brake B1, and therefore, the intersection of the vertical line Y1 and the horizontal line X1; Since the point where the vertical line representing the third rotating element RE3 rotated integrally with the input shaft 16, that is, the straight line connecting the intersection of the vertical line Y3 and the horizontal line X2, intersects the vertical line Y4 is on the horizontal line XG1, second intermediate output path M2 is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 38, a fifth rotary element RE5 is the rotational speed _{N G1} is connected to the second intermediate output path M2 by the engagement of the third clutch C3, the eighth rotary element RE8 third brake B3 Since the rotation speed is set to “0” by the engagement, the straight line connecting the intersection of the vertical line Y5 and the horizontal line XG1 and the intersection of the vertical line Y8 and the horizontal line X1 intersects the vertical line Y7 (2nd). The rotational speed of the output shaft 26 is shown.

  In the third gear, the sixth rotating element RE6 is connected to the first intermediate output path M1 by the engagement of the second clutch C2 to be set to the rotation speed “1”, and the eighth rotating element RE8 is connected to the third brake B3. Since the rotation speed is set to “0” by the engagement, the point (3rd) where the straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the intersection of the vertical line Y8 and the horizontal line X1 intersects the vertical line Y7 is The rotational speed of the output shaft 26 is shown.

In the fourth speed gear stage, in the first transmission unit 36, the first rotational element RE1 is set to the rotational speed “0” by the engagement of the first brake B1, so that the first speed element 36, as in the second speed gear stage, second intermediate output path M2 is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 38, a fifth rotary element RE5 is the rotational speed _{N G1} is connected to the second intermediate output path M2 by the engagement of the third clutch C3, sixth rotary element RE6 and the second clutch C2 Is connected to the first intermediate output path M1 and the rotation speed is “1”, so that a straight line connecting the intersection of the vertical line Y5 and the horizontal line XG1 and the intersection of the vertical line Y6 and the horizontal line X2 is vertical. The rotation speed of the output shaft 26 is indicated by a point (4th) intersecting the line Y7.

  In the fifth gear stage, the fifth rotation element RE5 is set to the rotation speed “1” by the engagement of the first clutch C1, and the sixth rotation element RE6 is set to the rotation speed “1” by the engagement of the second clutch C2. Therefore, the rotation speed of the output shaft 26 is indicated by the point (5th) at which the straight line connecting the intersection of the vertical line Y5 and the horizontal line X2 and the intersection of the vertical line Y6 and the horizontal line X2 intersects the vertical line Y7.

In the sixth speed gear stage, in the first transmission unit 36, the first rotational element RE1 is set to the rotational speed “0” by the engagement of the first brake B1, and therefore, as in the second speed gear stage, second intermediate output path M2 is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 38, the sixth rotary element RE6 is the rotational speed of "1" by the engagement of the second clutch C2, the eighth rotary element RE8 and the rotational speed _{N G1} by engagement of the fourth clutch C4 Therefore, the rotation speed of the output shaft 26 is indicated by the point (6th) at which the straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the intersection of the vertical line Y8 and the horizontal line XG1 intersects the vertical line Y7. .

In the seventh speed gear stage, in the first transmission unit 36, the first rotation element RE1 is set to the rotation speed “0” by the engagement of the first brake B1, and therefore, as in the second speed gear stage, second intermediate output path M2 is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 38, a fifth rotary element RE5 is the rotational speed _{N G1} by engagement of the third clutch C3, also the eighth rotary element RE8 rotational speed rotational speed by the engagement of the fourth clutch C4 because are N _G1, the intersection of the vertical line Y5 and horizontal XG1, that connects the intersection of the vertical line Y8 and horizontal XG1 straight line intersects the vertical line Y7 by (7th), the rotational speed of the output shaft 26 Is shown.

In the eighth speed gear stage, in the first transmission unit 36, the second rotation element RE2 is set to the rotation speed “0” by the engagement of the second brake B2, and therefore, the intersection of the vertical line Y2 and the horizontal line X1; Since the point where the vertical line representing the third rotation element RE3 rotated integrally with the input shaft 16, that is, the straight line connecting the intersection of the vertical line Y3 and the horizontal line X2, intersects the vertical line Y4 is on the horizontal line XG2, 2 The intermediate output path M2 is rotated at the rotational speed _NG2 . And in the 2nd transmission part 38, since the 3rd clutch C3 and the 4th clutch C4 are engaged similarly to the 7th speed gear stage, the intersection of the vertical line Y5 and the horizontal line XG2, and the vertical line Y8 and the horizontal line The rotation speed of the output shaft 26 is indicated by a point (8th) at which the straight line connecting the intersection with XG2 intersects the vertical line Y7.

  In the reverse gear, the fifth rotation element RE5 is set to the rotation speed “1” by the engagement of the first clutch C1, and the sixth rotation element RE6 is set to the rotation speed “0” of the fourth brake B4. A negative rotation speed of the output shaft 26 is indicated by a point (Rev) at which a straight line connecting the intersection of Y5 and the horizontal line X2 and the intersection of the vertical line Y6 and the horizontal line X1 intersects the vertical line Y7.

As described above, according to the present embodiment, the four sets of the first planetary gear unit 18, the second planetary gear unit 20, the third planetary gear unit 22, and the fourth planetary gear unit 24 have a large transmission ratio width. Thus, a small-sized planetary gear type multi-stage transmission for a vehicle that is capable of 8 forward speeds with appropriate speed ratio steps can be obtained. That is, the respective gear ratios γ are changed in a substantially equal ratio to obtain excellent speed increasing characteristics or acceleration characteristics by switching the gear stage, and the speed ratio width of the transmission 10 (= γ ₁ / γ ₈ ). Since it is set to a relatively large value, for example, “6.604”, for example, a small vehicular planetary gear type multi-stage transmission 10 that can achieve both high speed running and uphill starting performance can be obtained.

  Further, according to the present embodiment, the reverse gear is established by engaging the first clutch C1 and the fourth brake B4, so that in addition to the eighth forward speed, the first reverse gear stage is obtained. It is done.

  Further, according to the present embodiment, the first planetary gear device 18, the second planetary gear device 20, the third planetary gear device 22, and the fourth planetary gear device 24 are sequentially arranged between the input shaft 16 and the output shaft 26. Since the output of the engine 8 is input to the input shaft 16 of the transmission 10 via the torque converter 14 with the lock-up clutch 13 as a fluid transmission device, a compact automatic transmission can be designed.

  Next, a second embodiment of the present invention will be described. In the following description, parts common to those in the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.

  FIG. 4 is a skeleton diagram illustrating the configuration of the transmission 40 according to the second embodiment of the present invention, and FIG. The second embodiment is different in the configuration of the first transmission unit 42, but the other configurations and engagement operations are the same as those of the first embodiment shown in FIGS. 1 to 3, and FIGS. The same effect as the embodiment shown is obtained. Below, the different part is demonstrated.

In the second embodiment, the first transmission unit 42 includes two sets of planetary gear devices, a first planetary gear device 44 and a second planetary gear device 46, as in the first embodiment. The device 44 is a double pinion type planetary gear device, and the second planetary gear device 46 is a single pinion type planetary gear device. The first planetary gear unit 44 includes a first sun gear S1, a plurality of pairs of first planetary gears P1 that mesh with each other, a first carrier CA1 that supports the first planetary gear P1 so as to be capable of rotating and revolving, and a first planetary gear P1. and a first ring gear R1 meshing with the first sun gear S1 Te, for example has a gear ratio [rho ₁ of about "0.338". The second planetary gear unit 46 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. And has a predetermined gear ratio ρ ₂ of about “0.406”, for example.

  In the first transmission unit 42, the first sun gear S1 and the second ring gear R2 are integrally connected, and are selectively connected to the transmission case 12 via the first brake B1, and the first carrier CA1 is The first ring gear R1 and the second sun gear S2 are integrally connected to the second intermediate output path M2, and the input shaft 16 and the first intermediate output path disposed concentrically with the input shaft 16 are connected to the second intermediate output path M2. The second carrier CA2 is selectively connected to the transmission case 12 via the second brake B2. In the first transmission unit 42 configured as described above, the rotation of the input shaft 16 is output to the second transmission unit 38 from at least one of the first intermediate output path M1 and the second intermediate output path M2. When the rotation of the input shaft 16 is output from the second intermediate output path M2, it is rotated at an increased speed with respect to the first intermediate output path M1 and output. Also in this embodiment, since the first intermediate output path M1 is connected to the input shaft 16, the first intermediate output path M1 is rotated at the same rotational speed as the input shaft 16. The rotational speed of the output path M1 does not need to be the same as the rotational speed of the input shaft 16.

In the transmission 40 configured as described above, in the same manner as in the above-described embodiment, for example, as shown in the engagement operation table of FIG. The reverse gear stage is selectively established, and a gear ratio γ that changes substantially in the same ratio as in the first embodiment is obtained for each gear stage. The gear ratio [rho ₁ of the first planetary gear unit _44, the gear ratio [rho ₂ of the second planetary gear _46, the gear ratio [rho ₃ of the third planetary gear unit _22, the gear ratio [rho ₄ of the fourth planetary gear set 24, the It is set so that such a gear ratio can be obtained.

  In the first transmission unit 42 in the collinear diagram of FIG. 5, in order from the left, the first rotating element RE1 includes a first sun gear S1 and a second ring gear R2, the second rotating element RE2 includes a second carrier CA2, and a third The rotating element RE3 is composed of a first ring gear R1 and a second sun gear S2, and the fourth rotating element RE4 is composed of a first carrier CA1. Based on these rotating elements, the alignment chart shown in FIG. 5 is different from the alignment chart shown in FIG. 3 described above only in the configuration of each rotating element, and is the same as the alignment chart. The explanation of the alignment chart of FIG. 5 is omitted.

  Next, a third embodiment of the present invention will be described. FIG. 6 is a skeleton diagram illustrating the configuration of the transmission 50 according to the third embodiment, and FIG. 7 is a collinear diagram illustrating the rotational speeds of the rotating elements at each gear stage. The third embodiment differs from the first and second embodiments described above in the configuration of the first transmission unit 52, but the other configurations and engagement operations are the same as those in the first and second embodiments. Yes, the same effects as those of the embodiments can be obtained. Below, the different part is demonstrated.

In the third embodiment, the first transmission unit 52 includes two sets of planetary gear devices, a first planetary gear device 54 and a second planetary gear device 56, as in the two previous embodiments. The planetary gear unit 54 is a double pinion type planetary gear unit, and the second planetary gear unit 56 is a single pinion type planetary gear unit. The first planetary gear unit 54 includes a first sun gear S1, a plurality of pairs of first planetary gears P1 that mesh with each other, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first planetary gear P1. and a first ring gear R1 meshing with the first sun gear S1 Te, for example has a gear ratio [rho ₁ of about "0.289". The second planetary gear unit 56 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. and a second ring gear R2 meshing with, for example, has a "0.511" approximately predetermined gear ratio [rho _2.

  In the first transmission unit 52, the first sun gear S1 and the second carrier CA2 are integrally connected, and are also connected to the input shaft 16 and a first intermediate output path arranged concentrically with the input shaft 16. The first carrier CA1 and the second sun gear S2 are integrally connected and selectively connected to the transmission case 12 via the first brake B1, and the first ring gear R1 is connected to the transmission case via the second brake B2. The second ring gear R2 is connected to the second intermediate output path M2. In the first transmission unit 52 configured in this manner, the rotation of the input shaft 16 is output to the second transmission unit 38 from the output path of either the first intermediate output path M1 or the second intermediate output path M2, and the input shaft When the 16 rotations are output from the second intermediate output path M2, the rotation speed is increased with respect to the first intermediate output path M1 and output. In the third embodiment, since the first intermediate output path M1 is connected to the input shaft 16, the first intermediate output path M1 is rotated at the same rotational speed as the input shaft 16. The rotational speed of the 1 intermediate output path M1 does not need to be the same as the rotational speed of the input shaft 16.

In the transmission 50 configured as described above, as in the above-described embodiment, for example, as shown in the engagement operation table of FIG. The reverse gear stage is selectively established, and a gear ratio γ that changes substantially in the same ratio as in the first embodiment is obtained for each gear stage. The gear ratio [rho ₁ of the first planetary gear unit _54, the gear ratio [rho ₂ of the second planetary gear _56, the gear ratio [rho ₃ of the third planetary gear unit _22, the gear ratio [rho ₄ of the fourth planetary gear set 24, the It is set so that such a gear ratio can be obtained.

  In order from the left in the first transmission unit 52 in the collinear diagram of FIG. 7, the first rotating element RE1 includes the first carrier CA1 and the second sun gear S2, the second rotating element RE2 includes the first ring gear R1, and the third The rotating element RE3 is composed of a first sun gear S1 and a second carrier CA2, and the fourth rotating element RE4 is composed of a second ring gear R2. Based on these rotating elements, the alignment chart shown in FIG. 7 is different from the alignment chart shown in FIG. 3 described above only in the configuration of each rotating element, and is the same as the alignment chart. The explanation of the alignment chart of FIG. 7 is omitted.

  Next, a fourth embodiment of the present invention will be described. FIG. 8 is a skeleton diagram illustrating the configuration of the transmission 60 of the fourth embodiment, and FIG. 9 is a collinear diagram showing the rotational speeds of the rotating elements at each gear stage. The fourth embodiment differs from the first to third embodiments described above in the configuration of the first transmission unit 62, but the other configurations and engagement operations are the same as those in the first to third embodiments. The same effect can be obtained. Below, the different part is demonstrated.

In the fourth embodiment, the first transmission unit 62 includes two sets of planetary gear devices, a first planetary gear device 64 and a second planetary gear device 66, as in the previous embodiment. The device 64 is a double pinion type planetary gear device, and the second planetary gear device 66 is a single pinion type planetary gear device. The first planetary gear unit 64 includes a first sun gear S1, a plurality of pairs of first planetary gears P1 that mesh with each other, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first planetary gear P1. and a first ring gear R1 meshing with the first sun gear S1 Te, for example has a gear ratio [rho ₁ of about "0.338". The second planetary gear device 66 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. and a second ring gear R2 meshing with, for example, has a "0.236" approximately predetermined gear ratio [rho _2.

  In the first transmission unit 62, the first sun gear S1 and the second ring gear R2 are integrally connected, and are selectively connected to the transmission case 12 via the first brake B1, and the first carrier CA1 and the second ring gear R2 are connected. The two sun gears S2 are integrated and connected to the second intermediate output path M2, and the first ring gear R1 is connected to the input shaft 16 and the first intermediate output path disposed concentrically with the input shaft 16, The two carrier CA2 is selectively coupled to the transmission case 12 via the second brake B2. In the fourth embodiment, since the first intermediate output path M1 is connected to the input shaft 16, the first intermediate output path M1 is rotated at the same rotational speed as the input shaft 16. The rotational speed of the 1 intermediate output path M1 does not need to be the same as the rotational speed of the input shaft 16.

In the transmission 60 configured as described above, as in the above-described embodiment, for example, as shown in the engagement operation table of FIG. The reverse gear stage is selectively established, and a gear ratio γ that changes substantially in the same ratio as in the first embodiment is obtained for each gear stage. The gear ratio [rho ₁ of the first planetary gear unit _64, the gear ratio [rho ₂ of the second planetary gear _66, the gear ratio [rho ₃ of the third planetary gear unit _22, the gear ratio [rho ₄ of the fourth planetary gear set 24, the It is set so that such a gear ratio can be obtained.

  In the first transmission unit 62 in the collinear diagram of FIG. 9, in order from the left, the first rotating element RE1 includes the first sun gear S1 and the second ring gear R2, the second rotating element RE2 includes the second carrier CA2, and the third The rotation element RE3 is composed of a first ring gear R1, and the fourth rotation element RE4 is composed of a first carrier CA1 and a second sun gear S2. Based on these rotating elements, the alignment chart shown in FIG. 9 is different from the alignment chart shown in FIG. 3 described above only in the configuration of each rotating element, and is the same as the alignment chart. The explanation of the alignment chart of FIG. 9 is omitted.

  Next, a fifth embodiment of the present invention will be described. FIG. 10 is a skeleton diagram illustrating the configuration of the transmission 70 of the fifth embodiment, and FIG. 11 is a collinear diagram showing the rotational speeds of the rotating elements at each gear stage. The fifth embodiment is different from the first to fourth embodiments described above in the configuration of the first transmission unit 72, but the other configurations and engagement operations are the same as those in the first to fourth embodiments. The same effect can be obtained. Below, the different part is demonstrated.

In the fifth embodiment, the first transmission unit 72 includes two sets of planetary gear devices, a first planetary gear device 74 and a second planetary gear device 76, as in the previous embodiment, both of which are single. This is a pinion type planetary gear device. The first planetary gear device 74 includes a first sun gear S1, a first planetary gear P1, a first carrier CA1 that supports the first planetary gear P1 so as to rotate and revolve, and a first sun gear S1 via the first planetary gear P1. and a first ring gear R1 meshing with, for example, has a gear ratio [rho ₁ of about "0.511". The second planetary gear device 76 includes a second sun gear S2 via a second sun gear S2, a second planetary gear P2, a second carrier CA2 that supports the second planetary gear P2 so as to rotate and revolve, and a second planetary gear P2. and a second ring gear R2 meshing with, for example, has a "0.236" approximately predetermined gear ratio [rho _2.

  In the first transmission unit 72, the first sun gear S1 and the second ring gear R2 are integrally connected, and are selectively connected to the transmission case 12 via the first brake B1, and the first carrier CA1 is input. The shaft 16 and the first intermediate output path disposed concentrically with the input shaft 16 are connected, the first ring gear R1 and the second sun gear S2 are integrated and connected to the second intermediate output path M2, The two carrier CA2 is selectively coupled to the transmission case 12 via the second brake B2. In the fifth embodiment, since the first intermediate output path M1 is connected to the input shaft 16, the first intermediate output path M1 is rotated at the same rotational speed as the input shaft 16. The rotational speed of the 1 intermediate output path M1 does not need to be the same as the rotational speed of the input shaft 16.

In the transmission 70 configured as described above, as in the above-described embodiment, for example, as shown in the engagement operation table of FIG. 2, one of the first to eighth gear stages or the eighth gear stage or The reverse gear stage is selectively established, and a gear ratio γ that changes substantially in the same ratio as in the first embodiment is obtained for each gear stage. The gear ratio [rho ₁ of the first planetary gear unit _74, the gear ratio [rho ₂ of the second planetary gear _76, the gear ratio [rho ₃ of the third planetary gear unit _22, the gear ratio [rho ₄ of the fourth planetary gear set 24, the It is set so that such a gear ratio can be obtained.

  In the first transmission unit 72 in the collinear diagram of FIG. 11, in order from the left, the first rotating element RE1 is composed of the first sun gear S1 and the second ring gear R2, the second rotating element RE2 is composed of the second carrier CA2, and the third The rotating element RE3 is composed of a first carrier CA1, and the fourth rotating element RE4 is composed of a first ring gear R1 and a second sun gear S2. Based on these rotating elements, the collinear chart shown in FIG. 11 is different from the collinear chart shown in FIG. 3 described above only in the configuration of each rotating element, and is the same as the collinear chart. The explanation of the alignment chart of FIG. 11 is omitted.

  Next, a sixth embodiment of the present invention will be described. FIG. 12 is a skeleton diagram illustrating the configuration of the transmission 80 of the sixth embodiment. The transmission 10 is suitably used as an FF or RR automatic transmission that is placed horizontally in a vehicle. In FIG. 12, the transmission 80 includes a first shaft 82 coupled to the input shaft 16 and rotated integrally therewith, and a second shaft 84 disposed in parallel to the first shaft 82. In the transmission 80, the first transmission unit 86 is mainly configured by the first counter gear pair 88, the second counter gear pair 90, and the first planetary gear unit 92, and the second transmission unit 94 includes the second transmission gear unit 94. The third planetary gear device 22 and the fourth planetary gear device 24 which are arranged on the shaft 84 and are the same as those in the above-described embodiment are mainly configured.

  The first counter gear pair 88 is a power transmission device that transmits the rotation of the first shaft 82 to the second shaft 84, and includes a first drive gear 96 that is provided on the first shaft 82 so as not to rotate relative to the second shaft 84, and a second drive gear 96. The shaft 84 includes a first driven gear 98 provided so as to be rotatable relative to the shaft 84 and driven by meshing with the first drive gear 96. The first driven gear 98 constitutes one member of the first intermediate output path M1, that is, a first intermediate output member. In the present embodiment, the first drive gear 96 and the first driven gear 98 have the same number of teeth, and the rotational speed of the input shaft 16 is output to the second transmission unit 94 at the same speed. (Ie, the reduction ratio is set to 1), but the gear ratio of the first counter gear pair 88 can be set to an arbitrary value.

  The second counter gear pair 90 functions as a speed increasing device that speeds up the rotation of the input shaft 16 and outputs it to the second transmission unit 94. It is arranged on the side far from the torque converter 14 in the axial direction. The second counter gear pair 90 is provided on the first shaft 82 so as to be rotatable relative to the first shaft 82, and is provided on the second shaft 84 so as to be rotatable relative to the second drive gear 100 functioning as a drive side rotating member. The second driven gear 102 has a smaller number of teeth than the gear 100 and meshes with the second drive gear 100 to function as a driven side rotating member. The second driven gear 102 constitutes one member of the second intermediate output path M2, that is, a second intermediate output member. In this embodiment, the reduction ratio of the second counter gear pair 90 is 0.662. However, this reduction ratio can be set to an arbitrary value within a range smaller than the reduction ratio of the first counter gear pair 88.

The first planetary gear device 92 is disposed on the first shaft 82 between the first counter gear pair 88 and the second counter gear pair 90. The first planetary gear device 92 is a planetary gear device having a stepped pinion, and has a diameter different from that of the first sun gear S1, the first planetary gear portion P1 meshing with the sun gear S1, and the first planetary gear portion P1. A stepped pinion SP having a second planetary gear portion P2 having a number of teeth (that is, a smaller diameter or a smaller number of teeth than the first planetary gear portion P1), and a ring gear meshing with the second planetary gear portion P2 of the stepped pinion SP. R2 and a first carrier CA1 that supports the stepped pinion SP so as to be able to rotate and revolve, and has a predetermined gear ratio ρ ₁ of about “0.250”, for example. Incidentally, the gear ratio ρ1 is the value is not actually provided a number of teeth _{Z S1} of the first sun gear S1 divided by the number of teeth _{Z R1} of the first ring gear _{R1 (= Z S1 / Z R1} ). The first carrier CA1 that supports the second planetary gear portion P2 is regarded as the second carrier CA2, and a second sun gear S2 that is not actually provided but meshes with the second planetary gear portion P2 is provided. It can be considered that the second planetary gear unit is configured by the second sun gear S2, the second planetary gear P2, the second carrier CA2, and the second ring gear R2. The second planetary gear device has a predetermined gear ratio ρ ₂ (= the number of teeth Z _{S2 of} the second sun gear _S2 / the number of teeth Z _R2 of the second ring gear _R2 ) of, for example, about “0.610”.

  In the first transmission 86, the first sun gear S1 is selectively connected to the transmission case 12 via the speed increasing brake B0 and is also selectively connected to the first carrier CA1 via the integrated clutch C0. Has been. The first carrier CA1 is also connected to the first shaft 82, and the second ring gear R2 is connected to the second drive gear 100. When the integrated clutch C0 is engaged and the first sun gear S1 and the first carrier CA1 are connected, the components of the first planetary gear device 92 are rotated together, so that the second drive gear 100 is rotated at the same rotational speed as the input shaft 16. On the other hand, when the speed increasing brake B0 is engaged, the sun gear S1 cannot be rotated, so that the second drive gear 100 is rotated at a rotational speed faster than that of the input shaft 16. In particular, since the first planetary gear device 92 includes the stepped pinion SP, a high speed increase ratio can be obtained at a low rotational speed of the stepped pinion SP. However, if a predetermined speed increase ratio can be obtained even if a single pinion gear is used, a planetary gear device having a single pinion gear may be used.

  In the first speed change portion 86 configured as described above, the rotation of the input shaft 16 is caused by the first intermediate output path M1 passing through the first counter gear pair 88 or the intermediate output path M2 passing through the second counter gear pair 90. When the rotation is output from at least one of the output paths to the second transmission unit 94 and the rotation of the input shaft 16 is output from the second intermediate output path M2, the rotation speed is increased with respect to the first intermediate output path M1. Output.

  As in the above-described embodiment, the second transmission unit 94 mainly composed of the third planetary gear unit 22 and the fourth planetary gear unit 24 has the third planetary gear unit 22 and the fourth planetary gear unit 24 as the first. Between the first driven gear 98 and the second driven gear 102, the third planetary gear device 22 is disposed on the first driven gear 98 side, and the fourth planetary gear device 24 is disposed on the second driven gear 102 side. The second transmission unit 94 further includes a first clutch C1, a second clutch C2, a third clutch C3, a fourth clutch C4, a third brake B3, and a fourth brake B4.

  In the second transmission unit 94, the first clutch C1 selectively connects the first driven gear 98 and the second shaft 84, and the second clutch C2 is between the first driven gear 98 and the fourth carrier CA4. The third clutch C3 selectively connects the second driven gear 102 and the second shaft 84, and the fourth clutch C4 selects between the second driven gear 102 and the third carrier CA3. Therefore, when at least one of the first clutch C1 and the second clutch C2 is engaged, the rotation of the input shaft 16 is transferred to the second transmission unit 94 via the first intermediate output path M1. When at least one of the third clutch C3 and the fourth clutch C4 is engaged, the rotation of the input shaft 16 is input to the second transmission unit 94 via the second intermediate output path M2.

  The third sun gear S3 is provided on the second shaft 84 so as not to rotate relative to the second shaft 84. The third carrier CA3 is selectively connected to the transmission case 12 via the third brake B3 and via the fourth clutch C4. The third ring gear R3 and the fourth carrier CA4 are integrally connected to the second driven gear 102 and selectively connected to the transmission case 12 via the fourth brake B4. S4 is provided on the second shaft 84 so as not to rotate relative to the second shaft 84, and the fourth ring gear R4 is integrally connected to a drive pinion gear 104 that functions as an output rotating member. The drive pinion gear 104 is engaged with a ring gear 108 that is rotated integrally with the differential device 106.

In the transmission 80 configured as described above, for example, as shown in the engagement operation table of FIG. 13, two to three selected from the clutches C0 to C4 and the brakes B0 and B3 to B4 are simultaneously provided. By being engaged, either the first speed gear stage (first gear stage) to the eighth speed gear stage (eighth gear stage) or the reverse gear stage (reverse gear stage) is selectively established. Thus, a gear ratio γ (= input shaft rotational speed N _IN / output shaft rotational speed N _OUT ) that changes in a substantially equal ratio is obtained for each gear stage.

That is, as shown in FIG. 13, by engagement of the first clutch C1 and the third brake B3, between the first intermediate output path M1 and the third sun gear S3 and the fourth sun gear S4, the third carrier CA3 and the transmission case. by between 12 are respectively connected, first speed ratio [gamma ₁ is the maximum value, for example, "3.842" is established. Further, due to the engagement of the integrated clutch C0, the third clutch C3, and the third brake B3, between the first shaft 82 and the second drive gear 100, the second driven gear 102 (second intermediate intermediate output path M2) and the second 3 between the sun gear S3 and fourth sun gear S4, third carrier by between CA3 and the transmission case 12 are respectively connected, the speed ratio gamma ₂ is smaller than the first gear value, for example, "2. The second speed gear stage of about 543 "is established. Further, due to the engagement of the second clutch C2 and the third brake B3, the third carrier CA3 and the transmission case 12 are provided between the first driven gear 98 (first intermediate output path M1) and the fourth carrier CA4 and the third ring gear R3. by are respectively connected between the third speed ratio [gamma ₃ is smaller, for example, about "1.737" than the second speed position, it is established. Further, due to the engagement of the integrated clutch C0, the second clutch C2, and the third clutch C3, between the first shaft 82 and the second drive gear 100, the first driven gear 98 (first intermediate output path M1) and the fourth between the carrier CA4, and the third ring gear R3, by between the second driven gear 102 (second intermediate output path M2) and the third sun gear S3 and fourth sun gear S4 are connected respectively, is the gear ratio gamma ₄ second The fourth speed gear stage which is smaller than the third speed gear stage, for example, about “1.218” is established. Further, due to the engagement of the first clutch C1 and the second clutch C2, the first driven gear 98 (first intermediate gear 98) (first intermediate output path M1) is connected between the third sun gear S3 and the fourth sun gear S4. By connecting the output path M1) to the fourth carrier CA4 and the third ring gear R3, the _fifth gear ratio γ5 is smaller than the fourth gear, for example, about “1.000”. A speed gear is established. Further, due to the engagement of the integrated clutch C0, the second clutch C2, and the fourth clutch C4, between the first shaft 82 and the second drive gear 100, the first driven gear 98 (first intermediate output path M1) and the fourth between the carrier CA4, and the third ring gear R3, by between the second driven gear 102 (second intermediate output path M2) and the third carrier CA3 is connected respectively, the gear ratio gamma ₆ is than the fifth gear The sixth speed gear stage having a smaller value, for example, about “0.822” is established. Further, due to the engagement of the integrated clutch C0, the third clutch C3, and the fourth clutch C4, the second driven gear 102 (second intermediate output path M2) and the third shaft are connected between the first shaft 82 and the second drive gear 100. between the sun gear S3 and fourth sun gear S4, by between the second driven gear 102 (second intermediate output path M2) and the third carrier CA3 is connected respectively, the gear ratio gamma ₇ is than the sixth gear The seventh gear stage having a smaller value, for example, “0.622”, is established. Also, the second driven gear is connected between the second driven gear 102 (second intermediate output path M2) and the third sun gear S3 and the fourth sun gear S4 by the engagement of the third clutch C3, the fourth clutch C4 and the speed increasing brake B0. 102 (second intermediate output path M2) and the third carrier CA3, and between the first sun gear S1 and the transmission case 12, respectively, the transmission ratio γ ₈ is smaller than the seventh speed gear stage. An eighth speed gear having a value, for example, “0.582” is established. In the first speed gear stage, the third speed gear stage, and the fifth speed gear stage, the integrated clutch C0 may be further engaged.

Further, due to the engagement of the first clutch C1 and the fourth brake B4, between the first driven gear 98 (first intermediate output path M1) and the third sun gear S3 and the fourth sun gear S4, the third ring gear R3 and the fourth carrier. By connecting CA4 and transmission case 12 respectively, a reverse gear stage in which the gear ratio γ _R is a value between the first speed gear stage and the second speed gear stage, for example, “2.875” is established. Be made. The gear ratio [rho ₁ of the first planetary gear unit _92, [rho _2, the gear ratio [rho ₃ of the third planetary gear unit _22, the gear ratio [rho ₄ of the fourth planetary gear set 24, the gear ratio as described above can be obtained It is set as follows.

As described above, in this embodiment, since each gear ratio γ is the same as that in the first embodiment, the gear ratio step is the same as that in the first embodiment, and each gear ratio γ is changed substantially in a ratio. Further, the transmission gear ratio width (= γ ₁ / γ ₈ ) is also set to a relatively large value, that is, “6.604”.

FIG. 14 is a collinear diagram that can represent, on a straight line, the relative relationship between the rotational speeds of the rotating elements that are connected in different gear stages in the transmission 80. The collinear chart of FIG. 14 is a two-dimensional coordinate indicating the relationship of the gear ratio ρ of each planetary gear device 92, 22, 24 in the horizontal axis direction, and indicating the relative rotational speed in the vertical axis direction. The horizontal line X1 indicates the rotational speed zero, and the horizontal line X2 above it indicates the rotational speed “1.0”, that is, the rotational speed of the input shaft 16. The vertical lines Y1 to Y8 represent the first to eighth rotating elements RE1 to RE8 in order from the left, the first rotating element RE1 is the first sun gear S1, and the second rotating element RE2 is actually Is provided with the second sun gear S2, the third rotating element RE3 is the first carrier CA1 and the second carrier CA2, the fourth rotating element RE4 is the second ring gear R2, and the fifth rotating element RE5. Are a third sun gear S3 and a fourth sun gear S4 that are connected to each other, a sixth rotating element RE6 is a third ring gear R3 and a fourth carrier CA4 that are connected to each other, and a seventh rotating element RE7 is a fourth ring gear. R8 and the eighth rotating element RE8 is the third carrier CA3. The intervals between the vertical lines Y1 to Y4 are respectively determined according to the gear ratios ρ ₁ and ρ ₂ of the first planetary gear device 92 described above, and the intervals between the vertical lines Y5 to Y8 are the third planetary gear device 22 and the fourth planetary gear device 22. It is determined according to the gear ratios ρ ₃ and ρ ₄ of the planetary gear unit 24, and the vertical axis interval of the collinear chart is ρ between the sun gear and the carrier, and is ρ between the carrier and the ring gear. It is prescribed as follows.

  If expressed using the above nomograph, the transmission 80 of the present embodiment selects the first rotation element RE1 (S1) as the transmission case 12 via the speed increasing brake B0 in the first transmission 86. The third rotating element RE3 (CA1, CA2) is configured to be connected to the input shaft 16 and the first intermediate output path M1. Further, since the fourth rotating element RE4 (R2) is connected to the second counter gear pair 90 (second intermediate output path M2), when passing through the fourth rotating element RE4, the input shaft 16 The rotation is increased and output to the second transmission unit 94. On the other hand, in the second transmission unit 94, the fifth rotation element RE5 (S3, S4) is selectively coupled to the first intermediate output path M1 via the first clutch C1 and via the third clutch C3. The sixth intermediate rotation path RE6 (R3, CA4) is selectively connected to the first intermediate output path M1 via the second clutch C2, and is selectively connected to the second intermediate output path M2 (second driven gear 102). The seventh rotating element RE7 (R4) is connected to the drive pinion gear 104 (output rotating member) via the fourth brake B4, and is connected to the transmission case 12 via the fourth brake B4. ) Is selectively coupled to the second intermediate output path M2 (second driven gear 102) via the fourth clutch C4, and the transmission via the third brake B3. And it is configured to be selectively coupled to the transmission case 12.

  Each speed gear stage will be described with reference to the collinear diagram of FIG. In the first speed gear stage, the fifth rotation element RE5 is connected to the first intermediate output path M1 by the engagement of the first clutch C1 and is set to the rotation speed “1”, and the eighth rotation element RE8 is connected to the third brake B3. Since it is connected to the transmission case 12 by engagement and the rotational speed is set to “0”, a straight line connecting the intersection of the vertical line Y5 and the horizontal line X2 and the intersection of the vertical line Y8 and the horizontal line X1 intersects the vertical line Y7. The rotational speed of the drive pinion gear 104 is indicated by the point (1st) to be performed.

In the second speed gear stage, in the first transmission 86, the third rotation element RE3 and the first rotation element RE1 that are rotated together with the input shaft 16 by the engagement of the integrated clutch C0 are coupled. Accordingly, the fourth rotation element RE4 is rotated at the rotation speed “1”, the rotation is increased by the second counter gear pair 90, and is output to the second transmission unit 94 at the rotation speed N _G1 . Then, the second transmitting portion 94, a fifth rotary element RE5 is the rotational speed _{N G1} is connected to the second intermediate output path M2 by the engagement of the third clutch C3, the eighth rotary element RE8 third brake B3 since the by engagement with the rotational speed "0", that a point on the vertical line Y5 indicative of the rotational speed N _G1, the line connecting the intersection of the vertical line Y8 and horizontal X1 intersects the vertical line Y7 ( 2nd) indicates the rotational speed of the drive pinion gear 104.

  In the third gear, the sixth rotating element RE6 is connected to the first intermediate output path M1 by the engagement of the second clutch C2 to be set to the rotation speed “1”, and the eighth rotating element RE8 is connected to the third brake B3. Since the rotation speed is set to “0” by the engagement, the point (3rd) where the straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the intersection of the vertical line Y8 and the horizontal line X1 intersects the vertical line Y7 is The rotational speed of the drive pinion gear 104 is shown.

In the fourth speed gear stage, in the first transmission 86, the third rotating element RE3 and the first rotating element RE1 are connected by the engagement of the integrated clutch C0. Therefore, as in the second speed gear stage. the second intermediate output path M2 (second driven gear 102) is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 94, a fifth rotary element RE5 is the rotational speed _{N G1} is connected to the second intermediate output path M2 by the engagement of the third clutch C3, sixth rotary element RE6 and the second clutch C2 since the engagement is connected to the first intermediate output path M1 is the rotational speed "1", connecting on the vertical line Y5 and point representing the rotational speed N _G1, and a point of intersection between the vertical line Y6 and the horizontal line X2 The rotational speed of the drive pinion gear 104 is indicated by a point (4th) where the straight line intersects the vertical line Y7.

  In the fifth gear stage, the fifth rotation element RE5 is set to the rotation speed “1” by the engagement of the first clutch C1, and the sixth rotation element RE6 is set to the rotation speed “1” by the engagement of the second clutch C2. Therefore, the rotational speed of the drive pinion gear 104 is indicated by the point (5th) at which the straight line connecting the intersection of the vertical line Y5 and the horizontal line X2 and the intersection of the vertical line Y6 and the horizontal line X2 intersects the vertical line Y7.

In the sixth speed gear stage, in the first transmission unit 86, the third rotation element RE3 and the first rotation element RE1 are connected by the engagement of the integrated clutch C0. Therefore, as in the second speed gear stage. the second intermediate output path M2 (second driven gear 102) is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 94, the sixth rotary element RE6 is the rotational speed of "1" by the engagement of the second clutch C2, the eighth rotary element RE8 and the rotational speed _{N G1} by engagement of the fourth clutch C4 since the, the intersection of the vertical line Y6 and horizontal X2, a point that connects on the vertical line Y8 and points representing the rotation speed N _G1 straight line intersects the vertical line Y7 by (6th), the rotational speed of the drive pinion gear 104 Is shown.

In the seventh speed gear stage, in the first transmission unit 86, the third rotating element RE3 and the first rotating element RE1 are connected by the engagement of the integrated clutch C0. Therefore, as in the second speed gear stage. the second intermediate output path M2 (second driven gear 102) is rotated at a rotational speed _{N G1.} Then, the second transmitting portion 94, a fifth rotary element RE5 is the rotational speed _{N G1} by engagement of the third clutch C3, also the eighth rotary element RE8 rotational speed rotational speed by the engagement of the fourth clutch C4 since it is N _G1, on the vertical line Y5 and point representing the rotational speed N _G1, point connecting the points on the vertical line Y8 represents the rotational speed N _G1 straight line intersects the vertical line Y7 by (7th), The rotational speed of the drive pinion gear 104 is shown.

At the eighth speed gear stage, in the first transmission unit 86, the first rotational element RE1 is set to the rotational speed “0” by the engagement of the speed increasing brake B0. Therefore, the intersection of the vertical line Y1 and the horizontal line X1; The rotation speed of the fourth rotation element RE4 is determined by the point where the vertical line representing the third rotation element RE3 rotated integrally with the input shaft 16, that is, the straight line connecting the intersection of the vertical line Y3 and the horizontal line X2 intersects the vertical line Y4. N _G0 is indicated. Further, the rotational speed N _G0 is increased by the second counter gear pair 90 and output to the second transmission unit 94 at the rotational speed N _G2 . Then, the second transmitting portion 94, similarly to the seventh gear, the third clutch C3 and fourth clutch C4 is engaged, the point representing the rotational speed N _G2 on the vertical line Y5, vertical line the point at which a straight line connecting the points representing the rotational speed N _G2 intersects the vertical line Y7 (8th) on Y8, the rotational speed of the drive pinion gear 104 is shown.

  In the reverse gear, the fifth rotation element RE5 is set to the rotation speed “1” by the engagement of the first clutch C1, and the sixth rotation element RE6 is set to the rotation speed “0” of the fourth brake B4. A negative rotation speed of the drive pinion gear 104 is indicated by a point (Rev) at which a straight line connecting the intersection of Y5 and the horizontal line X2 and the intersection of the vertical line Y6 and the horizontal line X1 intersects the vertical line Y7.

As described above, according to the present embodiment, the three planetary gear devices 92, 22, 24 and the second counter gear pair 90 can increase the gear ratio range and the gear ratio step can be appropriately advanced 8. A small planetary gear type multi-stage transmission for a vehicle capable of high speed is obtained. That is, each gear ratio γ is changed in a substantially equal ratio to obtain an excellent speed increasing characteristic or acceleration characteristic by switching the gear stage, and the speed ratio width (= γ ₁ / γ ₈ ) of the transmission 80 is increased. Since it is set to a relatively large value, for example, “6.604”, for example, a small vehicular planetary gear type multi-stage transmission 10 that can achieve both high speed running and uphill starting performance can be obtained.

  Further, according to the present embodiment, the reverse gear is established by engaging the first clutch C1 and the fourth brake B4, so that in addition to the eighth forward speed, the first reverse gear stage is obtained. It is done.

  The transmission 80 of the present embodiment has a first shaft 82 connected to the input shaft 16 and a second shaft 84 parallel to the first shaft 82, and the first planetary gear device 92 is a first shaft 82. The third planetary gear device 22 and the fourth planetary gear device 24 are arranged on the second shaft 84 and are arranged on the second shaft 84 to increase the speed between the first shaft 82 and the second shaft 84. 90 and the output of the engine 8 is input to the input shaft 16 of the transmission 80 via the torque converter 14 with the lock-up clutch 13 as a fluid transmission device, so that a compact automatic transmission can be designed. It becomes possible.

  Next, a seventh embodiment of the present invention will be described. FIG. 15 is a skeleton diagram illustrating the configuration of the transmission 110 according to the seventh embodiment of the present invention, and FIG. 16 is a collinear diagram illustrating the rotational speed of the rotating element at each gear stage. In the seventh embodiment, the configuration of the second transmission unit 112 is different, but other configurations and engagement operations are the same as those of the sixth embodiment, and the same effects as those of the sixth embodiment can be obtained. Below, the different part is demonstrated.

In the seventh embodiment, the second transmission unit 112 includes two sets of planetary gear devices, a third planetary gear device 114 and a fourth planetary gear device 116. The third planetary gear unit 114 and the fourth planetary gear unit 116 are both single-pinion type planetary gear units, and the third planetary gear unit 114 includes the third sun gear S3, the third planetary gear P3, and the third planetary gear unit. A third carrier CA3 that supports P3 so as to rotate and revolve, and a third ring gear R3 that meshes with the third sun gear S3 via a third planetary gear P3, for example, a predetermined gear ratio ρ of about “0.352”. ₃ has a fourth planetary gear set 116, fourth sun gear S4, a fourth planet gear P4, a fourth carrier CA4 which rotatably and revolvably supports the fourth planetary gear P4, via the fourth planetary gear P4 the fourth and a fourth ring gear R4 meshing with the sun gear S4, for example has a gear ratio [rho ₄ of about "0.350" Te.

  Also in the second transmission unit 112, the first clutch C1 selectively connects between the first driven gear 98 and the second shaft 84, and the second clutch C2 is between the first driven gear 98 and the fourth carrier CA4. The third clutch C3 selectively connects the second driven gear 102 and the second shaft 84, and the fourth clutch C4 selects between the second driven gear 102 and the third carrier CA3. Therefore, when at least one of the first clutch C1 and the second clutch C2 is engaged, the rotation of the input shaft 16 is transferred to the second transmission unit 94 via the first intermediate output path M1. When at least one of the third clutch C3 and the fourth clutch C4 is engaged, the rotation of the input shaft 16 is input to the second transmission unit 94 via the second intermediate output path M2.

  The third sun gear S3 is provided on the second shaft 84 so as not to rotate relative to the second shaft 84. The third carrier CA3 is integrally connected to the fourth ring gear R4 and the drive pinion gear 104, and the third ring gear R3 is connected via the third brake B3. The transmission case 12 is selectively connected to the second driven gear 102 via the fourth clutch C4, and the fourth sun gear S4 is provided on the second shaft 84 so as not to rotate relative thereto.

In the transmission 110 configured as described above, as in the above-described sixth embodiment, for example, as shown in the engagement operation table of FIG. Alternatively, the reverse gear stage is selectively established, and a gear ratio γ (= input shaft rotational speed N _IN / output shaft rotational speed N _OUT ) that changes in a substantially equal ratio can be obtained for each gear stage. ing. The gear ratio [rho ₁ of the first planetary gear unit _92, [rho _2, the gear ratio of the third planetary gear set 114 [rho _3, the gear ratio [rho ₄ of the fourth planetary gear set 116, so that the gear ratios can be achieved It is set.

  In the second transmission unit 112 in the collinear diagram of FIG. 16, in order from the left, the fifth rotating element RE5 includes a third sun gear S3 and a fourth sun gear S4, and the sixth rotating element RE6 includes a fourth carrier CA4. The rotating element RE7 is composed of a third carrier CA3 and a fourth ring gear R4, and the eighth rotating element RE8 is composed of a third ring gear R3. Based on these rotating elements, the alignment chart shown in FIG. 16 differs from the alignment chart shown in FIG. 14 only in the configuration of each rotating element, and is the same as the alignment chart. The explanation of the alignment chart of FIG. 16 is omitted.

  Next, an eighth embodiment of the present invention will be described. FIG. 17 is a skeleton diagram illustrating the configuration of the transmission 120 according to the eighth embodiment of the present invention, and FIG. 18 is a collinear diagram illustrating the rotational speeds of the rotating elements at each gear stage. In the eighth embodiment, the configuration of the second transmission unit 122 is different, but other configurations and engagement operations are the same as those in the sixth embodiment and the seventh embodiment, and the same effects as those embodiments are obtained. can get. Below, the different part is demonstrated.

In the eighth embodiment, the second transmission unit 122 includes two sets of planetary gear devices, a third planetary gear device 124 and a fourth planetary gear device 126. The third planetary gear unit 124 is a double pinion type planetary gear unit, and the fourth planetary gear unit 126 is a single pinion type planetary gear unit. The third planetary gear unit 124 includes a third sun gear S3, a plurality of pairs of third planetary gears P3 that mesh with each other, a third carrier CA3 that supports the third planetary gear P3 so as to rotate and revolve, and a third planetary gear P3. third and a third ring gear R3 meshing with the sun gear S3, for example has a gear ratio [rho ₃ of about "0.548" Te. The fourth planetary gear unit 126 includes a fourth sun gear S4, a fourth planetary gear P4, a fourth carrier CA4 that supports the fourth planetary gear P4 so as to be capable of rotating and revolving, and a fourth sun gear S4 via the fourth planetary gear P4. And has a predetermined gear ratio ρ ₄ of about “0.350”, for example.

  Also in the second transmission unit 122, the first clutch C1 selectively connects the first driven gear 98 and the second shaft 84, and the second clutch C2 is between the first driven gear 98 and the fourth carrier CA4. Are selectively linked. The third clutch C3 selectively connects the second driven gear 102 and the third carrier CA3, and the fourth clutch C4 selectively connects the second driven gear 102 and the third carrier CA3. Therefore, when at least one of the first clutch C1 and the second clutch C2 is engaged, the rotation of the input shaft 16 is input to the second transmission unit 94 via the first intermediate output path M1, and the third transmission When at least one of the clutch C3 and the fourth clutch C4 is engaged, the rotation of the input shaft 16 is input to the second transmission unit 94 via the second intermediate output path M2.

The third sun gear S3 is provided so as to be rotatable relative to the second shaft 84, and the third carrier CA3 is selectively connected to the second driven gear 102 via the third clutch C3. 84, the third ring gear R3 and the fourth carrier CA4 are integrally connected, and are selectively connected to the transmission case 12 via the fourth brake B4, and the second clutch C2. The fourth sun gear S4 is provided on the second shaft 84 so as not to rotate relative to the first driven gear 98, and the fourth ring gear R4 is integrally connected to the drive pinion gear 104. The second shaft 84 is selectively coupled to the transmission case 12 via the third brake B3.

In the transmission 120 configured as described above, as in the above-described sixth to seventh embodiments, for example, as shown in the engagement operation table of FIG. 13, the first speed gear to the eighth speed gear. Any one of the gears or the reverse gear is selectively established, and a gear ratio γ (= input shaft rotational speed N _IN / output shaft rotational speed N _OUT ) that changes approximately in a ratio is obtained for each gear stage. It is like that. The gear ratio [rho ₁ of the first planetary gear unit _92, [rho _2, the gear ratio of the third planetary gear set 124 [rho _3, the gear ratio [rho ₄ of the fourth planetary gear set 126, so that the gear ratios can be achieved It is set.

  In the second transmission section 122 in the collinear diagram of FIG. 18, in order from the left, the fifth rotating element RE5 includes the third carrier CA3 and the fourth sun gear S4, and the sixth rotating element RE6 includes the third ring gear R3 and the fourth carrier CA4. The seventh rotation element RE7 is composed of a fourth ring gear R4, and the eighth rotation element RE8 is composed of a third sun gear S3. Based on these rotating elements, the collinear chart shown in FIG. 18 differs from the collinear chart shown in FIG. 14 only in the configuration of each rotating element, and is the same as the collinear chart. The explanation of the alignment chart of FIG. 18 is omitted.

  Next, a ninth embodiment of the present invention will be described. FIG. 19 is a skeleton diagram illustrating the configuration of the transmission 130 according to the ninth embodiment of the present invention, and FIG. The ninth embodiment is different in the configuration of the second transmission unit 132, but the other configurations and engagement operations are the same as those in the sixth to eighth embodiments, and the same effects as those embodiments are obtained. . Below, the different part is demonstrated.

In the ninth embodiment, the second transmission unit 132 includes two sets of planetary gear units, a third planetary gear unit 134 and a fourth planetary gear unit 136. The third planetary gear unit 134 is a double pinion type planetary gear unit, and the fourth planetary gear unit 136 is a single pinion type planetary gear unit. The third planetary gear unit 134 includes a third sun gear S3, a plurality of pairs of third planetary gears P3 that mesh with each other, a third carrier CA3 that supports the third planetary gear P3 so as to rotate and revolve, and a third planetary gear P3. third and a third ring gear R3 meshing with the sun gear S3, for example has a gear ratio [rho ₃ of about "0.424" Te. The fourth planetary gear device 136 includes a fourth sun gear S4, a fourth planetary gear P4, a fourth carrier CA4 that supports the fourth planetary gear P4 so as to rotate and revolve, and a fourth sun gear S4 via the fourth planetary gear P4. And has a predetermined gear ratio ρ ₄ of about “0.350”, for example.

  Also in the second transmission portion 132, the first clutch C1 selectively connects between the first driven gear 98 and the second shaft 84, and the second clutch C2 is between the first driven gear 98 and the fourth carrier CA4. Are selectively linked. The third clutch C3 selectively connects the second driven gear 102 and the second shaft 84, and the fourth clutch C4 selectively connects the second driven gear 102 and the third sun gear S3. Therefore, when at least one of the first clutch C1 and the second clutch C2 is engaged, the rotation of the input shaft 16 is input to the second transmission unit 94 via the first intermediate output path M1, and the third transmission When at least one of the clutch C3 and the fourth clutch C4 is engaged, the rotation of the input shaft 16 is input to the second transmission unit 94 via the second intermediate output path M2.

  The third sun gear S3 is also selectively connected to the transmission case 12 via the third brake B3, and the third carrier CA3 and the fourth carrier CA4 are connected integrally and via the fourth brake B4. Selectively coupled to the transmission case 12 and selectively coupled to the first driven gear 98 via the second clutch C2, the third ring gear R3 is integrally coupled to the fourth ring gear R4 and the drive pinion gear 104; The fourth sun gear S4 is provided on the second shaft 84 so as not to be relatively rotatable.

  The third planetary gear unit 134 and the fourth planetary gear unit 136 may be so-called Ravigneaux type planetary gear trains. That is, the third carrier CA3 and the fourth carrier CA4 are constituted by common parts, the third ring gear R3 and the fourth ring gear R4 are constituted by common parts, and the fourth planetary gear P4. May also serve as any one of a pair of third planetary gears P3 that mesh with each other. If the third planetary gear unit 134 and the fourth planetary gear unit 136 are Ravigneaux type planetary gear trains, the number of parts and the axial length can be further reduced.

In the transmission 130 configured as described above, as in the above-described sixth to eighth embodiments, for example, as shown in the engagement operation table of FIG. 13, the first speed gear to the eighth speed gear. Any one of the gears or the reverse gear is selectively established, and a gear ratio γ (= input shaft rotational speed N _IN / output shaft rotational speed N _OUT ) that changes approximately in a ratio is obtained for each gear stage. It is like that. The gear ratio [rho ₁ of the first planetary gear unit _92, [rho _2, the gear ratio of the third planetary gear set 134 [rho _3, the gear ratio [rho ₄ of the fourth planetary gear set 136, so that the gear ratios can be achieved It is set.

  In the second transmission section 132 in the collinear diagram of FIG. 20, in order from the left, the fifth rotating element RE5 is composed of the fourth sun gear S4, and the sixth rotating element RE6 is composed of the third carrier CA3 and the fourth carrier CA4. The rotating element RE7 is composed of a third ring gear R3 and a fourth ring gear R4, and the eighth rotating element RE8 is composed of a third sun gear S3. Based on these rotating elements, the collinear chart shown in FIG. 20 differs from the collinear chart shown in FIG. 14 only in the configuration of each rotating element, and is the same as the collinear chart. The explanation of the alignment chart of FIG. 20 is omitted.

  Next, a tenth embodiment of the present invention will be described. FIG. 21 is a skeleton diagram illustrating the configuration of the transmission 140 according to the tenth embodiment of the present invention, and FIG. The tenth embodiment differs from the sixth to ninth embodiments described above in the axial relative arrangement of the first counter gear pair 88, the second counter gear pair 90, and the first planetary gear unit 92 in the first transmission unit 142. Although different and the configuration of the second transmission unit 144 is different, other configurations and engagement operations are the same as those in the sixth to ninth embodiments, and the same effects as those embodiments can be obtained. Below, the different part is demonstrated.

  In the first transmission unit 86 of the sixth to ninth embodiments described above, the first counter gear pair 88, the first planetary gear device 92, and the second counter gear pair 90 are arranged in this order from the torque converter 14 side. However, in the tenth embodiment, the first transmission unit 142 is arranged in the order of the first planetary gear unit 92, the second counter gear pair 90, and the first counter gear pair 88 from the torque converter 14 side. However, the reduction ratio of the first counter gear pair 88 and the second counter gear pair 90 and the configuration of the first planetary gear unit 92 are the same as those in the sixth to ninth embodiments.

The second transmission unit 144 of the present embodiment includes two sets of planetary gear devices, a third planetary gear device 146 and a fourth planetary gear device 148. The third planetary gear unit 146 is a double pinion type planetary gear unit, and the fourth planetary gear unit 148 is a single pinion type planetary gear unit. The third planetary gear unit 146 includes a third sun gear S3, a plurality of pairs of third planetary gears P3 that mesh with each other, a third carrier CA3 that supports the third planetary gear P3 so as to be capable of rotating and revolving, and a third planetary gear P3. third and a third ring gear R3 meshing with the sun gear S3, for example has a gear ratio [rho ₃ of about "0.548" Te. The fourth planetary gear device 148 includes a fourth sun gear S4, a fourth planetary gear P4, a fourth carrier CA4 that supports the fourth planetary gear P4 so as to rotate and revolve, and a fourth sun gear S4 via the fourth planetary gear P4. And has a predetermined gear ratio ρ ₄ of about “0.352”, for example.

  In the second transmission portion 144, the third sun gear S3 and the fourth ring gear R4 are integrally connected, and are selectively connected to the second driven gear 102 via the fourth clutch C4, and the third brake. The third carrier CA3 is selectively connected to the first driven gear 98 via the first clutch C1 and the second driven gear via the third clutch C3. The third ring gear R3 is selectively connected to the first driven gear 98 via the second clutch C2 and selectively connected to the transmission case 12 via the fourth brake B4. The fourth sun gear S4 is provided so as not to rotate relative to the second shaft 84, and the fourth carrier CA4 is a drive pinion. Ya 104 and are integrally connected.

In the transmission 140 configured as described above, as in the above-described sixth to ninth embodiments, for example, as shown in the engagement operation table of FIG. 13, the first speed gear to the eighth speed gear. Any one of the gears or the reverse gear is selectively established, and a gear ratio γ (= input shaft rotational speed N _IN / output shaft rotational speed N _OUT ) that changes approximately in a ratio is obtained for each gear stage. It is like that. The gear ratio [rho ₁ of the first planetary gear unit _92, [rho _2, the gear ratio of the third planetary gear set 146 [rho _3, the gear ratio [rho ₄ of the fourth planetary gear set 148, so that the gear ratios can be achieved It is set.

  In the second transmission section 144 in the collinear diagram of FIG. 22, in order from the left, the fifth rotating element RE5 includes the third carrier CA3 and the fourth sun gear S4, and the sixth rotating element RE6 includes the third ring gear R3, The rotating element RE7 is composed of a fourth carrier CA4, and the eighth rotating element RE8 is composed of a third sun gear S3 and a fourth ring gear R4. Based on these rotating elements, the collinear chart shown in FIG. 22 differs from the collinear chart shown in FIG. 14 only in the configuration of each rotating element, and is the same as the collinear chart. Description of the alignment chart of FIG. 22 is omitted.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, in the transmissions 10, 40, 50, 60, 70, 80, 110, 120, 130, and 140 in the above-described embodiment, the forward eight-speed gear stage is established, but the eight-speed gear stage is established. Except for any one of them, the seventh forward speed may be established.

  Further, in the transmissions 10, 40, 50, 60, 70, 80, 110, 120, 130, 140 of the above-described embodiment, the engine 8 and the torque converter 14 are directly connected via the crankshaft 9, For example, it only needs to be operatively connected via a gear, a belt, or the like, and does not need to be arranged on a common axis. The engine 8 may be another driving force source such as an electric motor.

  Further, in the transmissions 10, 40, 50, 60, 70, 80, 110, 120, 130, and 140 of the above-described embodiments, at least one of the clutches C0 to C4 and the brakes B0 to B4 is provided with a one-way clutch. May be provided in series or in parallel. In this way, shift control becomes easy. Further, at least one of the clutches C0 to C4 and the brakes B0 to B4 may be replaced with a one-way clutch. Even in this way, a temporary shift can be obtained.

  In the above-described embodiment, the torque converter 14 with the lock-up clutch 13 is provided between the engine 8 and the input shaft 16 as a fluid transmission device. However, the lock-up clutch 13 may not be provided. . Further, instead of the torque converter 14, a fluid coupling, a magnetic powder type electromagnetic clutch, a multi-plate or a single-plate hydraulic clutch may be provided.

  In the collinear chart of the above-described embodiment, the vertical lines Y1 to Y8 are sequentially arranged from the left to the right, but may be sequentially arranged from the right to the left. Further, the horizontal axis X2 corresponding to the rotational speed “1” is arranged above the horizontal axis X1 corresponding to the rotational speed zero, but the horizontal axis X2 may be arranged below the horizontal axis X1.

  In the above-described embodiment, the clutch C or the brake B as the engagement element is a hydraulic friction engagement device, but may be an electromagnetic engagement device such as an electromagnetic clutch or a magnetic powder clutch.

  In the sixth to tenth embodiments described above, the counter gear pair 90 functions as a speed increasing device. However, instead of the counter gear pair 90, the rotation of the first shaft 82 is increased by a chain or a belt. Alternatively, a type of power transmission device that transmits to the second shaft 84 may be used.

  Further, in the sixth to tenth embodiments described above, one or more planetary gear devices may be provided on the first shaft 82.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a skeleton diagram illustrating a configuration of a main part of a planetary gear type multi-stage transmission for a vehicle that is an embodiment of the present invention. 2 is a chart showing the relationship between the transmission gear stage of the planetary gear type multi-stage transmission for the vehicle of the embodiment of FIG. 1 and the operation of the hydraulic friction engagement device necessary to establish it. It is a collinear diagram explaining the action of the planetary gear type multi-stage transmission for the vehicle of the embodiment of FIG. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles in 2nd Example of this invention. It is an alignment chart explaining the action | operation of the planetary gear type multistage transmission for vehicles of 2nd Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multi-stage transmission for vehicles in 3rd Example of this invention. It is an alignment chart explaining the action | operation of the planetary gear type multistage transmission for vehicles of 3rd Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles in 4th Example of this invention. It is an alignment chart explaining the action | operation of the planetary gear type multistage transmission for vehicles of 4th Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles in 5th Example of this invention. It is an alignment chart explaining the action | operation of the planetary gear type multistage transmission for vehicles of 5th Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles which is 6th Example of this invention. It is a table | surface which shows the relationship between the transmission gear stage of the planetary gear type multistage transmission for vehicles of 6th Example, and the action | operation of the hydraulic frictional engagement apparatus required in order to establish it. It is a collinear diagram explaining the action | operation of the planetary gear type multistage transmission for vehicles of 6th Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multi-stage transmission for vehicles in 7th Example of this invention. It is a collinear diagram explaining the action | operation of the planetary gear type multistage transmission for vehicles of 7th Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles which is 8th Example of this invention. It is a collinear diagram explaining the action | operation of the planetary gear type multistage transmission for vehicles of 8th Example. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles in 9th Example of this invention. It is a collinear diagram explaining the operation of the planetary gear type multi-stage transmission for a vehicle of the ninth embodiment. It is a skeleton diagram explaining the principal part structure of the planetary gear type multistage transmission for vehicles which is 10th Example of this invention. It is a collinear diagram explaining the action | operation of the planetary gear type multistage transmission for vehicles of 10th Example.

Explanation of symbols

8: Engine 10, 40, 50, 60, 70, 80, 110, 120, 130, 140: Planetary gear type multi-stage transmission for vehicle 12: Transmission case (non-rotating member)
14: Torque converter (fluid transmission)
16: Input shaft (input rotating member)
18, 44, 54, 64, 74, 92: First planetary gear unit 20, 46, 56, 66, 76: Second planetary gear unit 22, 114, 124, 134, 146: Third planetary gear unit 24, 116 126, 136, 148: Fourth planetary gear unit 26: Output shaft (output rotating member)
36, 42, 52, 62, 72, 86, 142: first transmission unit 38, 94, 112, 122, 132, 144: second transmission unit 104: drive pinion gear 104 (output rotating member)
M1: First intermediate output path M2: Second intermediate output path

Claims (47)

A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
A first intermediate output path; and two intermediate output paths, a second intermediate output path that is rotated at one of two speed-up speed ratios with respect to the first intermediate output path. A first transmission unit that outputs the rotation of at least one of the two intermediate output paths;
The sun gear, the carrier, and part of the ring gear of the third planetary gear device and the fourth planetary gear device are connected to each other to constitute four rotating elements, and the rotational speed of the four rotating elements is linearly determined. In the collinear chart that can be represented, when the four rotating elements are sequentially designated as a fifth rotating element, a sixth rotating element, a seventh rotating element, and an eighth rotating element from one end to the other end, The five-rotation element is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch, and the sixth rotation element is The seventh rotating element is connected to the output rotating member selectively through the second clutch, the eighth rotating element is connected to the second intermediate output path through the fourth clutch. Selectively connect to While with the a second transmitting portion which is selectively connected to a non-rotating member through a third brake, and includes,
A plurality of shift speeds are established by selectively switching between engagement and disengagement states of the clutch and brake and changing a selection state of the two types of speed-up gear ratios of the second intermediate output path. Planetary gear type multi-stage transmission for vehicles. The planetary gear type multi-stage transmission for a vehicle according to claim 1,
At least eight forward speeds by selectively switching the engagement and disengagement states of the first to fourth clutches and the third brake and changing the selection state of the two types of speed increase gear ratios of the second intermediate output path A planetary gear type multi-stage transmission for a vehicle, characterized in that The vehicular planetary gear type multi-stage transmission according to claim 2,
When the first clutch and the third brake are engaged, the first gear stage having the largest gear ratio is established, the third clutch and the third brake are engaged , and the second intermediate rotational state of the output path, the two of the types of speed increasing gear ratio is selected the rotation state of being is accelerated by the speed increasing gear ratio of relatively small side shift than the first gear position by Rukoto A second gear having a smaller ratio is established, and the second clutch and the third brake are engaged to establish a third gear having a smaller gear ratio than the second gear. The second clutch and the third clutch are engaged , and the rotation state of the second intermediate output path is increased at a relatively small speed increasing speed ratio among the two speed increasing speed ratios. Rotation state -Option is the fourth gear position gear ratio than the third gear position is smaller by Rukoto is is established, the speed ratio than the fourth gear position by said first clutch and said second clutch are engaged A fifth shift stage having a smaller gear ratio is established, and by engaging the second clutch and the fourth clutch, a sixth shift stage having a smaller gear ratio than the fifth shift stage is established, and the third shift stage is established. The clutch and the fourth clutch are engaged , and the rotational state of the second intermediate output path is increased at a relatively small speed increasing speed ratio among the two kinds of speed increasing speed ratios. and seventh shift stage is selected the rotation state smaller speed ratio than the sixth gear position by Rukoto is is established, the third clutch and the fourth clutch is engaged, and the second intermediate output Sutra Is selected from among the two types of speed-up gear ratios, the speed-up ratio being higher than that of the seventh gear. small eighth gear position vehicular planetary gear type step-variable transmission, wherein Rukoto allowed to established. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
The sun gear, the carrier, and a part of the ring gear of the first planetary gear device and the second planetary gear device are connected to each other to constitute four rotating elements, and the rotational speeds of the four rotating elements are linearly adjusted. In the collinear chart that can be represented, when the four rotating elements are sequentially designated as a first rotating element, a second rotating element, a third rotating element, and a fourth rotating element from one end to the other end, The one rotation element is selectively connected to the non-rotation member via the first brake, the second rotation element is selectively connected to the non-rotation member via the second brake, and the third rotation element is the input A first transmission unit coupled to the rotating member and the first intermediate output path, wherein the fourth rotating element is coupled to the second intermediate output path;
The sun gear, the carrier, and part of the ring gear of the third planetary gear device and the fourth planetary gear device are connected to each other to constitute four rotating elements, and the rotational speed of the four rotating elements is linearly determined. In the collinear chart that can be represented, when the four rotating elements are sequentially designated as a fifth rotating element, a sixth rotating element, a seventh rotating element, and an eighth rotating element from one end to the other end, The five-rotation element is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch, and the sixth rotation element is The seventh rotating element is connected to the output rotating member selectively through the second clutch, the eighth rotating element is connected to the second intermediate output path through the fourth clutch. Selectively connect to While with the a second transmitting portion which is selectively connected to a non-rotating member through a third brake, and includes,
A planetary gear type multi-stage transmission for a vehicle, wherein a forward 8-speed gear stage is established by selectively switching between engagement and disengagement of the clutch and brake. The vehicular planetary gear type multi-stage transmission according to claim 4,
When the first clutch and the third brake are engaged, the first gear stage having the largest gear ratio is established, and the third clutch, the first brake, and the third brake are engaged. To establish a second gear stage having a gear ratio smaller than that of the first gear stage, and a third gear ratio having a gear ratio smaller than that of the second gear stage is established by engaging the second clutch and the third brake. A gear stage is established, and the second clutch, the third clutch, and the first brake are engaged to establish a fourth gear stage having a gear ratio smaller than that of the third gear stage. When the first clutch and the second clutch are engaged, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established, and the second clutch By engaging the fourth clutch and the first brake, a sixth shift stage having a smaller gear ratio than the fifth shift stage is established, and the third clutch, the fourth clutch, and the first brake are established. Is engaged to establish a seventh shift speed having a smaller gear ratio than the sixth shift speed, and the third clutch, the fourth clutch, and the second brake are engaged to cause the seventh shift speed to be established. A planetary gear type multi-stage transmission for a vehicle, wherein an eighth speed stage having a speed ratio smaller than that of the speed stage is established. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
A first intermediate output path for outputting rotation of the input rotation member from a first intermediate output member;
A second intermediate output path for increasing the speed of rotation of the input rotating member with respect to the first intermediate output path by a speed increasing device;
A plurality of gears, and one of the plurality of gears is connected to the drive side rotation member of the speed increasing device, and the rotation of the input rotating member is increased or the speed increasing device is driven at a constant speed. A first speed changer comprising: a speed increasing gear device that outputs to the side rotating member;
The sun gear, the carrier, and part of the ring gear of the third planetary gear device and the fourth planetary gear device are connected to each other to constitute four rotating elements, and the rotational speed of the four rotating elements is linearly determined. In the collinear chart that can be represented, when the four rotating elements are sequentially designated as a fifth rotating element, a sixth rotating element, a seventh rotating element, and an eighth rotating element from one end to the other end, The five-rotation element is selectively connected to the first intermediate output path via a first clutch and is selectively connected to the second intermediate output path via a third clutch, and the sixth rotation element is The seventh rotating element is connected to the output rotating member selectively through the second clutch, the eighth rotating element is connected to the second intermediate output path through the fourth clutch. Selectively connect to While with the a second transmitting portion which is selectively connected to a non-rotating member through a third brake, and includes,
A planetary gear type multi-stage transmission for a vehicle, wherein a forward 8-speed gear stage is established by selectively switching between engagement and disengagement of the clutch and brake. The vehicle planetary gear type multi-stage transmission according to claim 6,
The speed increasing gear device includes three rotating members of a first sun gear, a first carrier, and a first ring gear, and the first rotating member of the three rotating members is made into a non-rotating member via a speed increasing brake. An integrated clutch that is selectively connected, the second rotating member is connected to the drive-side rotating member of the speed increasing device, and selectively connects the first rotating member and the third rotating member; A planetary gear type multi-stage transmission for a vehicle, which is a first planetary gear device in which a first rotating member and a third rotating member are selectively rotated integrally. The vehicular planetary gear type multi-stage transmission according to claim 7 ,
By engaging the first clutch and the third brake, the first gear stage having the largest speed ratio is established, and by engaging the integrated clutch, the third clutch, and the third brake. A third gear position having a smaller gear ratio than the first gear position is established, and a third gear ratio having a smaller gear ratio than the second gear position is established by engaging the second clutch and the third brake. A first gear is established, and a fourth gear having a smaller gear ratio than the third gear is established by engaging the integrated clutch, the second clutch, and the third clutch, and the first clutch And by engaging the second clutch, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established, and the integrated clutch, When the second clutch and the fourth clutch are engaged, a sixth gear having a smaller gear ratio than the fifth gear is established, and the integrated clutch, the third clutch, and the fourth clutch are engaged. As a result, a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established, and the third clutch, the fourth clutch, and the speed increasing brake are engaged with each other than the seventh shift stage. A planetary gear type multi-stage transmission for a vehicle characterized in that the eighth speed stage having a small gear ratio is established. A preceding claims vehicular planetary gear type step-variable transmission according to any one of claims 5,
The first transmission unit and the second transmission unit are arranged in series,
In the second transmission unit, the third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear. , A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the third carrier, the fourth planetary gear device comprising a fourth sun gear, a fourth carrier, and a fourth ring gear. Single pinion type planetary gear unit,
The fifth rotating element is the third sun gear and the fourth sun gear, the sixth rotating element is the third ring gear and the fourth carrier, the seventh rotating element is the fourth ring gear, A planetary gear type multi-stage transmission for a vehicle, wherein the eighth rotating element is the third carrier. The vehicle planetary gear type multi-stage transmission according to claim 4 ,
In the first transmission unit, the first planetary gear device and the second planetary gear device are disposed concentrically, and the first planetary gear device includes a first sun gear, a first carrier, and a first ring gear. A single pinion type planetary gear device, wherein the second planetary gear device is a single pinion type planetary gear device comprising a second sun gear, a second carrier, and a second ring gear,
The first rotating element is the first ring gear and the second sun gear; the second rotating element is the first carrier; the third rotating element is the first sun gear and the second carrier; A planetary gear type multi-stage transmission for a vehicle, wherein the fourth rotating element is the second ring gear. The vehicle planetary gear type multi-stage transmission according to claim 4 ,
The first transmission unit includes the first planetary gear unit and the second planetary gear unit concentrically arranged, and the first planetary gear unit includes a first sun gear, a first carrier, and a first ring gear. A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the first carrier, the second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear. Single pinion type planetary gear unit,
The first rotating element is the first sun gear and the second ring gear; the second rotating element is the second carrier; the third rotating element is the first ring gear and the second sun gear; A planetary gear type multi-stage transmission for a vehicle, wherein the fourth rotating element is the first carrier. The vehicle planetary gear type multi-stage transmission according to claim 4 ,
The first transmission unit includes the first planetary gear unit and the second planetary gear unit concentrically arranged, and the first planetary gear unit includes a first sun gear, a first carrier, and a first ring gear. A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the first carrier, the second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear. Single pinion type planetary gear unit,
The first rotating element is the first carrier and the second sun gear; the second rotating element is the first ring gear; the third rotating element is the first sun gear and the second carrier; A planetary gear type multi-stage transmission for a vehicle, wherein the fourth rotating element is the second ring gear. The vehicle planetary gear type multi-stage transmission according to claim 4 ,
The first transmission unit includes the first planetary gear unit and the second planetary gear unit concentrically arranged, and the first planetary gear unit includes a first sun gear, a first carrier, and a first ring gear. A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the first carrier, the second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear. Single pinion type planetary gear unit,
The first rotating element is the first sun gear and the second ring gear, the second rotating element is the second carrier, the third rotating element is the first ring gear, and the fourth rotating element is A planetary gear type multi-stage transmission for a vehicle, characterized in that it is the first carrier and the second sun gear. The vehicle planetary gear type multi-stage transmission according to claim 4 ,
In the first transmission unit, the first planetary gear device and the second planetary gear device are disposed concentrically, and the first planetary gear device includes a first sun gear, a first carrier, and a first ring gear. A single pinion type planetary gear device, wherein the second planetary gear device is a single pinion type planetary gear device comprising a second sun gear, a second carrier, and a second ring gear,
The first rotating element is the first sun gear and the second ring gear, the second rotating element is the second carrier, the third rotating element is the first carrier, and the fourth rotating element is A planetary gear type multi-stage transmission for a vehicle, characterized in that the first ring gear and the second sun gear. A preceding claims vehicular planetary gear type step-variable transmission according to any one of claims 3,
A first axis coupled to the input rotation member, and a second axis parallel to the first axis;
The first speed change portion includes a driving side rotating member provided on the first shaft and a driven side rotating member provided on the second shaft and rotated by the driving side rotating member. Equipped with equipment,
The planetary gear type multi-stage transmission for a vehicle, wherein the second transmission portion is disposed on the second shaft. A planetary gear type multi-speed transmission for a vehicle according to any one of claims 6 to 8,
A first axis coupled to the input rotation member, and a second axis parallel to the first axis;
The speed increasing device of the first transmission unit includes a driving side rotating member provided on the first shaft, and a driven side rotating member provided on the second shaft and rotated by the driving side rotating member. Have
The speed increasing gear device of the first transmission unit is disposed on the first shaft,
The planetary gear type multi-stage transmission for a vehicle, wherein the second transmission portion is disposed on the second shaft. The planetary gear type multi-stage transmission for a vehicle according to claim 15 or 16,
In the second transmission unit, the third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear. , A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the third carrier, the fourth planetary gear device comprising a fourth sun gear, a fourth carrier, and a fourth ring gear. Single pinion type planetary gear unit,
The fifth rotating element is the third sun gear and the fourth sun gear, the sixth rotating element is the third ring gear and the fourth carrier, the seventh rotating element is the fourth ring gear, A planetary gear type multi-stage transmission for a vehicle, wherein the eighth rotating element is the third carrier. The planetary gear type multi-stage transmission for a vehicle according to claim 15 or 16,
In the second transmission unit, the third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear. Single pinion type planetary gear device, and the fourth planetary gear device is a single pinion type planetary gear device having a fourth sun gear, a fourth carrier, and a fourth ring gear,
The fifth rotating element is the third sun gear and the fourth sun gear, the sixth rotating element is the fourth carrier, the seventh rotating element is the third carrier and the fourth ring gear, and A planetary gear type multi-stage transmission for a vehicle, wherein the eight-rotating element is the third ring gear. The planetary gear type multi-stage transmission for a vehicle according to claim 15 or 16,
In the second transmission unit, the third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear. , A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the third carrier, the fourth planetary gear device comprising a fourth sun gear, a fourth carrier, and a fourth ring gear. Single pinion type planetary gear unit,
The fifth rotating element is the third carrier and the fourth sun gear, the sixth rotating element is the third ring gear and the fourth carrier, the seventh rotating element is the fourth ring gear, A planetary gear type multi-stage transmission for vehicles, wherein the eighth rotating element is the third sun gear. The planetary gear type multi-stage transmission for a vehicle according to claim 15 or 16,
In the second transmission unit, the third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear. , A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the third carrier, the fourth planetary gear device comprising a fourth sun gear, a fourth carrier, and a fourth ring gear. Single pinion type planetary gear unit,
The fifth rotating element is the fourth sun gear, the sixth rotating element is the third carrier and the fourth carrier, the seventh rotating element is the third ring gear and the fourth ring gear, A planetary gear type multi-stage transmission for a vehicle, wherein the eighth rotating element is the third sun gear. The planetary gear type multi-stage transmission for a vehicle according to claim 20,
The third carrier, the fourth carrier, the third ring gear, and the fourth ring gear are configured by a common member, and the planetary gear of the fourth planetary gear device meshes with the third planetary gear device. A planetary gear type multi-stage transmission for a vehicle, which serves as any one of a pair of planetary gears. The planetary gear type multi-stage transmission for a vehicle according to claim 15 or 16,
In the second transmission unit, the third planetary gear device and the fourth planetary gear device are arranged concentrically, and the third planetary gear device includes a third sun gear, a third carrier, and a third ring gear. , A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the third carrier, the fourth planetary gear device comprising a fourth sun gear, a fourth carrier, and a fourth ring gear. Single pinion type planetary gear unit,
The fifth rotating element is the third carrier and the fourth sun gear, the sixth rotating element is the third ring gear, the seventh rotating element is the fourth carrier, and the eighth rotating element is the A planetary gear type multi-stage transmission for a vehicle, characterized by being a third sun gear and a fourth ring gear. A preceding claims vehicular planetary gear type step-variable transmission according to any one of claims 22,
The sixth rotating element is selectively coupled to a non-rotating member via a fourth brake;
A planetary gear type multi-stage transmission for a vehicle, wherein the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission unit that outputs at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier engages the fourth clutch. A second transmission unit that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake;
While
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake,
The first transmission unit is
A single pinion type first planetary gear device including a first sun gear, a first carrier, and a first ring gear; and a single pinion type second planetary gear device including a second sun gear, a second carrier, and a second ring gear; Including
The first ring gear and the second sun gear are selectively connected to a non-rotating member via a first brake, and the first carrier is selectively connected to a non-rotating member via a second brake. A planetary gear type multi-stage transmission for a vehicle, wherein the sun gear and the second carrier are connected to the input rotating member and a first intermediate output path, and the second ring gear is connected to a second intermediate output path. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission unit that outputs at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier engages the fourth clutch. A second transmission unit that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake;
While
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake,
The first transmission unit is
A double pinion type first planetary gear device having a first sun gear, a first carrier, and a first ring gear, and having a pair of meshing planetary gears rotatably supported by the first carrier; a second sun gear; A single-pinion type second planetary gear device having two carriers and a second ring gear,
The first sun gear and the second ring gear are selectively connected to a non-rotating member via a first brake, and the second carrier is selectively connected to a non-rotating member via a second brake. A planetary gear type multi-stage transmission for a vehicle, wherein the ring gear and the second sun gear are connected to the input rotating member and the first intermediate output path, and the first carrier is connected to the second intermediate output path. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission unit that outputs at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier engages the fourth clutch. A second transmission unit that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake;
While
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake,
The first transmission unit is
A double pinion type first planetary gear device having a first sun gear, a first carrier, and a first ring gear, and having a pair of meshing planetary gears rotatably supported by the first carrier; a second sun gear; A single-pinion type second planetary gear device having two carriers and a second ring gear,
The first carrier and the second sun gear are selectively connected to a non-rotating member via a first brake, and the first ring gear is selectively connected to a non-rotating member via a second brake. A planetary gear type multi-stage transmission for a vehicle, wherein the sun gear and the second carrier are connected to the input rotating member and a first intermediate output path, and the second ring gear is connected to a second intermediate output path. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission unit that outputs at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier engages the fourth clutch. A second transmission unit that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake;
While
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake,
The first transmission unit is
A double pinion type first planetary gear device having a first sun gear, a first carrier, and a first ring gear, and having a pair of meshing planetary gears rotatably supported by the first carrier; a second sun gear; A single-pinion type second planetary gear device having two carriers and a second ring gear,
The first sun gear and the second ring gear are selectively connected to a non-rotating member via a first brake, and the second carrier is selectively connected to a non-rotating member via a second brake. A planetary gear type multi-stage transmission for a vehicle, wherein the ring gear is connected to the input rotation member and the first intermediate output path, and the first carrier and the second sun gear are connected to the second intermediate output path. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, and that shifts the rotation of the input rotation member and outputs the rotation from the output rotation member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission unit that outputs at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier engages the fourth clutch. A second transmission unit that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake;
While
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake,
The first transmission unit is
A single pinion type first planetary gear device including a first sun gear, a first carrier, and a first ring gear; and a single pinion type second planetary gear device including a second sun gear, a second carrier, and a second ring gear; Including
The first sun gear and the second ring gear are selectively connected to a non-rotating member via a first brake, and the second carrier is selectively connected to a non-rotating member via a second brake. A planetary gear type multi-stage transmission for a vehicle, wherein the carrier is connected to the input rotating member and the first intermediate output path, and the first ring gear and the second sun gear are connected to the second intermediate output path. A vehicular planetary gear type step-variable transmission according to any one of claims 24 through claim 28,
A planetary gear type for a vehicle, wherein at least a seventh forward speed is established by selectively switching the engagement and release states of the first to fourth clutches and the first to third brakes. Multi-stage transmission. A vehicular planetary gear type step-variable transmission according to any one of claims 24 through claim 29,
When the first clutch and the third brake are engaged, the first gear stage having the largest gear ratio is established, and the third clutch, the first brake, and the third brake are engaged. To establish a second gear stage having a gear ratio smaller than that of the first gear stage, and a third gear ratio having a gear ratio smaller than that of the second gear stage is established by engaging the second clutch and the third brake. A gear stage is established, and the second clutch, the third clutch, and the first brake are engaged to establish a fourth gear stage having a gear ratio smaller than that of the third gear stage. When the first clutch and the second clutch are engaged, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established, and the second clutch By engaging the fourth clutch and the first brake, a sixth shift stage having a smaller gear ratio than the fifth shift stage is established, and the third clutch, the fourth clutch, and the first brake are established. Is engaged to establish a seventh shift speed having a smaller gear ratio than the sixth shift speed, and the third clutch, the fourth clutch, and the second brake are engaged to cause the seventh shift speed to be established. A planetary gear type multi-stage transmission for a vehicle, wherein an eighth speed stage having a speed ratio smaller than that of the speed stage is established. A vehicular planetary gear type step-variable transmission according to any one of claims 24 through claim 30,
The third ring gear and the fourth carrier are selectively connected to a non-rotating member via a fourth brake, and the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for a vehicle. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
A first shaft coupled to the input rotating member;
A second axis parallel to the first axis;
A first intermediate output path for outputting rotation of the input rotation member from a first intermediate output member; a drive side rotation member provided on the first shaft; and a drive side rotation member provided on the second shaft A speed increasing device for increasing the rotation of the input rotating member, and a second speed increasing device for output to the first intermediate output path by the speed increasing device. An intermediate output path and a plurality of gears, and one of the plurality of gears is connected to a drive side rotation member of the speed increasing device, and the rotation of the input rotation member is increased or constant speed A first speed changer including a speed increasing gear device that outputs to a driving side rotating member of the speed increasing device;
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third carrier engages the fourth clutch. A second speed changer that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake,
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and release states of the clutch and brake. The vehicular planetary gear type multi-stage transmission according to claim 32 ,
The speed increasing gear device includes three rotating members of a first sun gear, a first carrier, and a first ring gear, and the first rotating member of the three rotating members is made into a non-rotating member via a speed increasing brake. An integrated clutch that is selectively connected, the second rotating member is connected to the drive-side rotating member of the speed increasing device, and selectively connects the first rotating member and the third rotating member; A planetary gear type multi-stage transmission for a vehicle, which is a first planetary gear device in which a first rotating member and a third rotating member are selectively rotated integrally. A vehicular planetary gear type multi-stage transmission according to claim 32 or claim 33 ,
The third ring gear and the fourth carrier are selectively connected to a non-rotating member via a fourth brake, and the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for a vehicle. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission that outputs via at least one of them,
A single pinion type third planetary gear device including a third sun gear, a third carrier, and a third ring gear, and a single pinion type fourth planetary gear device including a fourth sun gear, a fourth carrier, and a fourth ring gear. Including
The third sun gear and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the third carrier and the fourth ring gear are connected to the output rotating member, and the third ring gear is connected to the fourth clutch via the fourth clutch. A second speed changer that is selectively connected to the second intermediate output path and selectively connected to the non-rotating member via a third brake,
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake ,
A first shaft coupled to the input rotation member; and a second shaft parallel to the first shaft;
The first transmission unit is
A first intermediate output path for outputting rotation of the input rotation member from a first intermediate output member;
A driving-side rotating member provided on the first shaft, and a driven-side rotating member provided on the second shaft and rotated by the driving-side rotating member, to accelerate the rotation of the input rotating member A speed increasing device,
A second intermediate output path that outputs the increased speed to the first intermediate output path by the speed increasing device;
A plurality of gears, and one of the plurality of gears is connected to the drive side rotation member of the speed increasing device, and the rotation of the input rotating member is accelerated or the speed increasing device is driven at a constant speed. vehicular planetary gear type step-variable transmission which is characterized that you have a speed increasing gear device that outputs to the side rotating member. The planetary gear type multi-stage transmission for a vehicle according to claim 35 ,
The fourth carrier is selectively connected to a non-rotating member via a fourth brake, and the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for vehicles. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission that outputs via at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third carrier and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, The third ring gear and the fourth carrier are selectively connected to the first intermediate output path via a second clutch, the fourth ring gear is connected to the output rotating member, and the third sun gear is connected to the fourth clutch. A second speed changer that is selectively connected to the second intermediate output path via a third brake and selectively connected to a non-rotating member via a third brake,
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake ,
A first shaft coupled to the input rotation member; and a second shaft parallel to the first shaft;
The first transmission unit is
A first intermediate output path for outputting rotation of the input rotation member from a first intermediate output member;
A driving-side rotating member provided on the first shaft, and a driven-side rotating member provided on the second shaft and rotated by the driving-side rotating member, to accelerate the rotation of the input rotating member A speed increasing device,
A second intermediate output path that outputs the increased speed to the first intermediate output path by the speed increasing device;
A plurality of gears, and one of the plurality of gears is connected to the drive side rotation member of the speed increasing device, and the rotation of the input rotating member is accelerated or the speed increasing device is driven at a constant speed. vehicular planetary gear type step-variable transmission which is characterized that you have a speed increasing gear device that outputs to the side rotating member. A vehicular planetary gear type multi-stage transmission according to claim 37 ,
The third ring gear and the fourth carrier are selectively connected to a non-rotating member via a fourth brake, and the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for a vehicle. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission that outputs via at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The fourth sun gear is selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch, and the third carrier and the The fourth carrier is selectively connected to the first intermediate output path via a second clutch, the third ring gear and the fourth ring gear are connected to the output rotating member, and the third sun gear is connected to the fourth clutch. And a second transmission part selectively connected to the second intermediate output path and selectively connected to the non-rotating member via a third brake,
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake ,
A first shaft coupled to the input rotation member; and a second shaft parallel to the first shaft;
The first transmission unit is
A first intermediate output path for outputting rotation of the input rotation member from a first intermediate output member;
A driving-side rotating member provided on the first shaft, and a driven-side rotating member provided on the second shaft and rotated by the driving-side rotating member, to accelerate the rotation of the input rotating member A speed increasing device,
A second intermediate output path that outputs the increased speed to the first intermediate output path by the speed increasing device;
A plurality of gears, and one of the plurality of gears is connected to the drive side rotation member of the speed increasing device, and the rotation of the input rotating member is accelerated or the speed increasing device is driven at a constant speed. vehicular planetary gear type step-variable transmission which is characterized that you have a speed increasing gear device that outputs to the side rotating member. The planetary gear type multi-stage transmission for a vehicle according to claim 39 ,
The third carrier, the fourth carrier, the third ring gear, and the fourth ring gear are configured by a common member, and the planetary gear of the fourth planetary gear device meshes with the third planetary gear device. A planetary gear type multi-stage transmission for a vehicle, which serves as any one of a pair of planetary gears. A planetary gear type multi-stage transmission for a vehicle according to claim 39 to claim 40 ,
The third carrier and the fourth carrier are selectively connected to a non-rotating member via a fourth brake, and the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for a vehicle. A planetary gear type multi-stage transmission for a vehicle that includes a plurality of planetary gear devices, that changes the speed of rotation of an input rotary member and outputs it from an output rotary member,
Two intermediate output paths, a first intermediate output path and a second intermediate output path that is rotated at an increased speed with respect to the first intermediate output path, and the rotation of the input rotation member is controlled by any of the two intermediate output paths. A first transmission that outputs via at least one of them,
A double pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear, and having a pair of meshing planetary gears rotatably supported by the third carrier; a fourth sun gear; A single-pinion type fourth planetary gear device having four carriers and a fourth ring gear,
The third carrier and the fourth sun gear are selectively connected to the first intermediate output path via a first clutch and selectively connected to the second intermediate output path via a third clutch. A 3-ring gear is selectively connected to the first intermediate output path via a second clutch, the fourth carrier is connected to the output rotating member, and the third sun gear and the fourth ring gear are connected via a fourth clutch. A second speed changer selectively connected to the second intermediate output path and selectively connected to a non-rotating member via a third brake,
A plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake ,
A first shaft coupled to the input rotation member; and a second shaft parallel to the first shaft;
The first transmission unit is
A first intermediate output path for outputting rotation of the input rotation member from a first intermediate output member;
A driving-side rotating member provided on the first shaft, and a driven-side rotating member provided on the second shaft and rotated by the driving-side rotating member, to accelerate the rotation of the input rotating member A speed increasing device,
A second intermediate output path that outputs the increased speed to the first intermediate output path by the speed increasing device;
A plurality of gears, and one of the plurality of gears is connected to the drive side rotation member of the speed increasing device, and the rotation of the input rotating member is accelerated or the speed increasing device is driven at a constant speed. vehicular planetary gear type step-variable transmission which is characterized that you have a speed increasing gear device that outputs to the side rotating member. The planetary gear type multi-stage transmission for a vehicle according to claim 42 ,
The third ring gear is selectively connected to a non-rotating member via a fourth brake, and the reverse gear is established by engaging the fourth brake and the first clutch. A planetary gear type multi-stage transmission for vehicles. A vehicular planetary gear type multi-stage transmission according to any one of claims 35 to 43 ,
The speed increasing gear device includes three rotating members of a first sun gear, a first carrier, and a first ring gear, and the first rotating member of the three rotating members is made into a non-rotating member via a speed increasing brake. An integrated clutch that is selectively connected, the second rotating member is connected to the drive-side rotating member of the speed increasing device, and selectively connects the first rotating member and the third rotating member; A planetary gear type multi-stage transmission for a vehicle, which is a first planetary gear device in which a first rotating member and a third rotating member are selectively rotated integrally. A claims 32 through the planetary gear type multi-speed transmission for a vehicle according to any one of claims 44,
A planetary gear type multi-stage transmission for a vehicle, wherein at least a seventh forward speed is established by selectively switching between engagement and disengagement of the clutch and brake. The planetary gear type multi-stage transmission for a vehicle according to claim 45 ,
By engaging the first clutch and the third brake, the first gear stage having the largest speed ratio is established, and by engaging the integrated clutch, the third clutch, and the third brake. A third gear position having a smaller gear ratio than the first gear position is established, and a third gear ratio having a smaller gear ratio than the second gear position is established by engaging the second clutch and the third brake. A first gear is established, and a fourth gear having a smaller gear ratio than the third gear is established by engaging the integrated clutch, the second clutch, and the third clutch, and the first clutch And by engaging the second clutch, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established, and the integrated clutch, When the second clutch and the fourth clutch are engaged, a sixth gear having a smaller gear ratio than the fifth gear is established, and the integrated clutch, the third clutch, and the fourth clutch are engaged. As a result, a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established, and the third clutch, the fourth clutch, and the speed increasing brake are engaged with each other than the seventh shift stage. A planetary gear type multi-stage transmission for a vehicle characterized in that the eighth speed stage having a small gear ratio is established. A preceding claims vehicular planetary gear type step-variable transmission according to any one of claims 46,
An output of the engine is input to the input rotating member via a fluid transmission device, and a planetary gear type multi-stage transmission for a vehicle.

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