JP4254413B2 - 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 can it be configured simply, the gear stage can be increased in number and the gear ratio range can be increased, but the gear ratio step to be switched is equal or close to it. It is desirable to be able to change the shape. 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.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to provide a planetary for a vehicle that can have a large transmission gear ratio range and that the transmission gear ratio step can be an appropriate forward speed of 7 or more. The object is to provide a gear type multi-stage transmission.

  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) The sun gear, the carrier, and the ring gear of the first planetary gear device to the fourth planetary gear device are connected to each other to form six rotating elements, and the rotational speeds of the six rotating elements are On the collinear chart that can be represented on a straight line, the six rotating elements are arranged in order from one end to the other end of the first rotating element, the second rotating element, the third rotating element, the fourth rotating element, and the fifth rotating element. When the element and the sixth rotating element are used, the first rotating element is selectively connected to the input rotating member via the fourth clutch and is selectively connected to the non-rotating member via the first brake. The second rotation is necessary Is selectively connected to the non-rotating member via the second brake, the third rotating element is selectively connected to the non-rotating member via the third brake, the first rotating element and the second rotating element. An input-side rotation element whose rotation is uniquely determined from the rotation of the rotation element, and an output-side rotation element whose rotation is uniquely determined from the rotation of the second rotation element and the sixth rotation element, the input-side rotation element And its output-side rotating element are selectively connected to each other via a third clutch to rotate together, and its fourth rotating element is selectively connected to the input rotating member via a second clutch. And is selectively connected to the non-rotating member via the fourth brake, the fifth rotating element is connected to the output rotating member, and the sixth rotating element is selected to the input rotating member via the first clutch. In It is binding, and a plurality of shift stage is established by switching selectively the (c) engagement of the clutch and brake, released state.

  According to a second aspect of the present invention that achieves the above object, in the first aspect, at least the seventh forward speed is achieved by selectively switching the engagement and release states of the first to third clutches and the first to fourth brakes. This is characterized in that the following shift stage is established.

  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, the third clutch, and the fourth brake. When the first clutch and the third brake are engaged, a second gear having a smaller gear ratio than the first gear is established, and the first clutch and the second 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 third gear stage is established by engaging the first clutch, the third clutch, and the first brake. A fourth gear stage having a smaller gear ratio is established, and the first clutch, the second clutch, and the first brake are engaged, thereby A fifth gear position having a smaller gear ratio than the fourth gear position is established, and the first clutch, the second clutch, and the third clutch are engaged, so that the gear ratio is smaller than the fifth gear position. The sixth shift stage is established, and the seventh shift stage having a smaller gear ratio than the sixth shift stage is established by engaging the second clutch, the third clutch, and the first brake. It is characterized by.

  According to a fourth aspect of the invention for achieving the above object, in the third aspect of the invention, an eighth gear ratio is smaller than that of the seventh speed step when the second clutch, the third clutch, and the second brake are engaged. The speed stage is established.

  According to a fifth aspect of the invention for achieving the above object, in any one of the first to fourth aspects, the reverse gear is established by engaging the third clutch, the fourth clutch, and the fourth brake. It is made to be made to be made.

  According to a sixth aspect of the invention for achieving the above object, in any one of the first to fifth aspects, the first planetary gear device 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 a carrier, wherein the second planetary gear device comprises a second sun gear, a second carrier, and a second ring gear; A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by two carriers, the third planetary gear device having a third sun gear, a third carrier, and a third ring gear. Type planetary gear device, wherein the fourth planetary gear device is a single pinion equipped with a fourth sun gear, a fourth carrier, and a fourth ring gear. The first rotating element is the first carrier and the second sun gear, the second rotating element is the first ring gear, the second ring gear and the third ring gear, The input rotation element of the third rotation element is the second carrier, the output rotation element of the third rotation element is the third carrier and the fourth ring gear, and the fourth rotation element is the first sun gear. The fifth rotating element is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear.

  According to a seventh aspect of the invention for achieving the above object, in any one of the first to fifth aspects, the first planetary gear device 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 a carrier, wherein the second planetary gear device comprises a second sun gear, a second carrier, and a second ring gear; A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by two carriers, the third planetary gear device having a third sun gear, a third carrier, and a third ring gear. Type planetary gear device, wherein the fourth planetary gear device is a single pinion equipped with a fourth sun gear, a fourth carrier, and a fourth ring gear. The first rotating element is the first carrier and the second carrier, the second rotating element is the first ring gear, the second ring gear and the third ring gear, The input rotation element of the third rotation element is the second sun gear, the output rotation element of the third rotation element is the third carrier and the fourth ring gear, and the fourth rotation element is the first sun gear. The fifth rotating element is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear.

  An eighth invention that achieves 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) The sun gear, the carrier, and the ring gear of the first planetary gear device to the fourth planetary gear device are connected to each other to form six rotating elements, and the six rotating elements rotate. In the collinear chart in which the speed can be expressed on a straight line, the six rotating elements are arranged in order from one end to the other end in the order of the first rotating element, the second rotating element, the third rotating element, the fourth rotating element, When the five-rotation element and the sixth rotation element are used, the first rotation element is selectively connected to the input rotation member via the fifth clutch and is selectively selected to the non-rotation member via the first brake. Connected, the second The element is selectively connected to the non-rotating member via the second brake, and the third rotating element is selectively connected to the input rotating member via the second clutch and non-rotating via the third brake. An input-side rotating element that is selectively coupled to the member and whose third rotating element is uniquely determined from the rotation of the first rotating element and the second rotating element; the second rotating element; and the second rotating element An output-side rotating element whose rotation is uniquely determined from the rotation of the six-rotating element, and the input-side rotating element and the output-side rotating element are selectively connected to each other via a fourth clutch to rotate integrally. The fourth rotating element is selectively connected to the input rotating member via a third clutch and is selectively connected to the non-rotating member via a fourth brake, and the fifth rotating element is Output times A sixth rotary element is selectively connected to the input rotary member via a first clutch, and (c) a plurality of clutches and brakes are selectively switched between engagement and release states. A shift stage is established.

  According to a ninth aspect of the invention that achieves the above object, in the eighth aspect of the invention, at least the seventh forward speed is achieved by selectively switching the engagement and release states of the first to fourth clutches and the first to fourth brakes. This is characterized in that the following shift stage is established.

  According to a tenth aspect of the invention for achieving the above object, in the ninth aspect of the invention, the first gear stage having the largest gear ratio is established by engaging the first clutch, the fourth clutch, and the fourth brake. When the first clutch and the third brake are engaged, a second gear having a smaller gear ratio than the first gear is established, and the first clutch and the second brake are engaged. As a result, a third gear stage having a smaller gear ratio than the second gear stage is established, and the third gear stage is engaged by engaging the first clutch, the fourth clutch, and the first brake. When the fourth gear stage having a smaller gear ratio is established and the first clutch, the second clutch, and the first brake are engaged, the front A fifth gear position having a smaller gear ratio than the fourth gear position is established, and the first clutch, the second clutch, and the fourth clutch are engaged, so that the gear ratio is greater than that of the fifth gear position. A small sixth gear is established, and a seventh gear having a smaller gear ratio than the sixth gear is established by engaging the third clutch, the fourth clutch, and the first brake. It is characterized by that.

  An eleventh aspect of the invention for achieving the object described above is the tenth aspect, wherein the second clutch, the fourth clutch, and the first brake are engaged, or the third clutch, the fourth clutch, By engaging the two brakes, an eighth speed stage having a smaller gear ratio than the seventh speed stage is established.

  In a twelfth aspect of the invention that achieves the above object, in any one of the eighth to eleventh aspects, the reverse gear is established by engaging the fourth clutch, the fifth clutch, and the fourth brake. It is made to be made to be made.

  The thirteenth invention for achieving the object is any one of the eighth to twelfth inventions, wherein the first planetary gear device 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 a carrier, wherein the second planetary gear device comprises a second sun gear, a second carrier, and a second ring gear; A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by two carriers, the third planetary gear device having a third sun gear, a third carrier, and a third ring gear. Type planetary gear unit, wherein the fourth planetary gear unit is a single planetary gear unit comprising a fourth sun gear, a fourth carrier, and a fourth ring gear. A first planetary gear device, wherein the first rotating element is the first carrier and the second sun gear, and the second rotating element is the first ring gear, the second ring gear, and the third ring gear; The input rotation element of the third rotation element is the second carrier, the output rotation element of the third rotation element is the third carrier and the fourth ring gear, and the fourth rotation element is the first sun gear. The fifth rotating element is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear.

  According to a fourteenth aspect of the present invention for achieving the above object, in any one of the eighth to twelfth aspects, the first planetary gear device 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 a first carrier, the second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear; A double pinion type planetary gear device having a pair of meshing planetary gears rotatably supported by the second carrier, wherein the third planetary gear device comprises a third sun gear, a third carrier, and a third ring gear. This is a single pinion type planetary gear device, and the fourth planetary gear device includes a fourth sun gear, a fourth carrier, and a fourth ring gear. A planetary gear unit of the gallpinion type, wherein the first rotating element is a first carrier and a second carrier thereof, and the second rotating element is a first ring gear, a second ring gear and a third ring gear thereof; The input rotation element of the third rotation element is the second sun gear, the output rotation element of the third rotation element is the third carrier and the fourth ring gear, and the fourth rotation element is the first sun gear. The fifth rotating element is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear.

  A fifteenth 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) a double pinion type first planetary gear device comprising 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; (c) a double pinion type second planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier; ) A single pinion type third planetary gear device having a third sun gear, a third carrier and a third ring gear; and (e) a single pinion having a fourth sun gear, a fourth carrier and a fourth ring gear. And (f) the first carrier and the second sun gear are selectively connected to the input rotation member via a fourth clutch and are not connected via a first brake. The first ring gear, the second ring gear, and the third ring gear are selectively connected to the non-rotating member via the second brake, and the second carrier and the third carrier are selectively connected to the rotating member. Is selectively connected to each other via a third clutch, its third carrier and its fourth ring gear are selectively connected to a non-rotating member via a third brake, and its first sun gear is connected via a second clutch. And selectively connected to the non-rotating member via a fourth brake, the fourth carrier being connected to the output rotating member, and the third carrier. And the fourth sun gear are selectively connected to the input rotating member via the first clutch, and (g) a plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake. It is made to be made to be made.

  A sixteenth 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) a double pinion type first planetary gear device comprising 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; (c) a double pinion type second planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier; ) A single pinion type third planetary gear device having a third sun gear, a third carrier and a third ring gear; and (e) a single pinion having a fourth sun gear, a fourth carrier and a fourth ring gear. And (f) the first carrier and the second carrier are selectively connected to the input rotation member via a fourth clutch and are not connected via a first brake. The first ring gear, the second ring gear, and the third ring gear are selectively connected to the non-rotating member via a second brake, and the second sun gear and the third carrier are selectively connected to the rotating member. Is selectively connected to each other via a third clutch, its third carrier and its fourth ring gear are selectively connected to a non-rotating member via a third brake, and its first sun gear is connected via a second clutch. And selectively connected to the non-rotating member via a fourth brake, the fourth carrier being connected to the output rotating member, and the third carrier. And the fourth sun gear are selectively connected to the input rotating member via the first clutch, and (g) a plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake. It is made to be made to be made.

  According to a seventeenth aspect of the invention that achieves the above object, in the fifteenth or sixteenth aspect of the invention, the engagement and release states of the first to third clutches and the first to fourth brakes are selectively switched. It is characterized in that at least a forward seventh speed is established.

  According to an eighteenth aspect of the present invention that achieves the above object, in the seventeenth aspect, the first gear stage having the largest gear ratio is established by engaging the first clutch, the third clutch, and the fourth brake. When the first clutch and the third brake are engaged, a second gear having a smaller gear ratio than the first gear is established, and the first clutch and the second 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 third gear stage is established by engaging the first clutch, the third clutch, and the first brake. A fourth gear stage having a smaller gear ratio is established, and the first clutch, the second clutch, and the first brake are engaged. A fifth gear position having a smaller gear ratio than the fourth gear position is established, and the first clutch, the second clutch, and the third clutch are engaged, and thereby the gear ratio is larger than that of the fifth gear position. A sixth gear with a smaller gear ratio is established, and a seventh gear having a smaller gear ratio than the sixth gear is established by engaging the second clutch, the third clutch, and the first brake. It is characterized by being able to.

  According to a nineteenth aspect of the invention that achieves the above object, according to the eighteenth aspect of the invention, an eighth gear ratio is smaller than the seventh speed step when the second clutch, the third clutch, and the second brake are engaged. The speed stage is established.

  According to a twentieth aspect of the invention for achieving the above object, in any one of the fifteenth to nineteenth aspects, the reverse gear is established by engaging the third clutch, the fourth clutch, and the fourth brake. It is made to be made to be made.

  A twenty-first 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 changes the rotation of the input rotating member and outputs it from the output rotating member. (B) a double pinion type first planetary gear device comprising 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; (c) a double pinion type second planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier; ) A single pinion type third planetary gear device having a third sun gear, a third carrier and a third ring gear; and (e) a single pinion having a fourth sun gear, a fourth carrier and a fourth ring gear. And (f) the first carrier and the second sun gear are selectively connected to the input rotation member via a fifth clutch and are not connected via a first brake. The first ring gear, the second ring gear, and the third ring gear are selectively connected to the non-rotating member via the second brake, and the second carrier and the third carrier are selectively connected to the rotating member. Are selectively connected to each other via a fourth clutch, and the second carrier is selectively connected to the input rotating member via a second clutch, and the third carrier and the fourth ring gear are third. The first sun gear is selectively connected to the input rotating member via a third clutch and is non-rotated via a fourth brake. Selectively coupled to a member, the fourth carrier is coupled to the output rotating member, the third sun gear and the fourth sun gear are selectively coupled to the input rotating member via a first clutch, (g ) It is characterized in that a plurality of shift speeds are established by selectively switching the engagement and release states of the clutch and brake.

A twenty-second 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) a double pinion type first planetary gear device comprising 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; (c) a double pinion type second planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier; ) A single pinion type third planetary gear device having a third sun gear, a third carrier and a third ring gear; and (e) a single pinion having a fourth sun gear, a fourth carrier and a fourth ring gear. And (f) the first carrier and the second carrier are selectively connected to the input rotating member via a fifth clutch and are not connected via a first brake. The first ring gear, the second ring gear, and the third ring gear are selectively connected to the non-rotating member via a second brake, and the second sun gear and the third carrier are selectively connected to the rotating member. Are selectively connected to each other via a fourth clutch, and the second sun gear is selectively connected to the input rotating member via a second clutch, and the third carrier and the fourth ring gear are third. The first sun gear is selectively connected to the input rotating member via a third clutch and is non-rotated via a fourth brake. Selectively coupled to a member, the fourth carrier is coupled to the output rotating member, the third sun gear and the fourth sun gear are selectively coupled to the input rotating member via a first clutch, (g ) It is characterized in that a plurality of shift stages are established by selectively switching the engagement and release states of the clutch and brake.

  A twenty-third invention that achieves the above object is the one according to the twenty-first invention or the twenty-second invention, by selectively switching the engagement and release states of the first to fourth clutches and the first to fourth brakes. It is characterized in that at least a forward seventh speed is established.

  According to a twenty-fourth aspect of the present invention that achieves the above object, in the twenty-third aspect, the first shift stage having the largest gear ratio is established by engaging the first clutch, the fourth clutch, and the fourth brake. When the first clutch and the third brake are engaged, a second gear having a smaller gear ratio than the first gear is established, and the first clutch and the second brake are engaged. As a result, a third gear stage having a smaller gear ratio than the second gear stage is established, and the third gear stage is engaged by engaging the first clutch, the fourth clutch, and the first brake. A fourth gear stage having a smaller gear ratio is established, and the first clutch, the second clutch, and the first brake are engaged. A fifth gear position having a smaller gear ratio than that of the fourth gear position is established, and the first clutch, the second clutch, and the fourth clutch are engaged, whereby the gear ratio is greater than that of the fifth gear position. A sixth gear with a smaller gear ratio is established, and the third gear, the fourth clutch, and the first brake are engaged to establish a seventh gear with a smaller gear ratio than the sixth gear. It is characterized by being able to.

  According to a twenty-fifth aspect of the invention for achieving the above object, in the twenty-fourth aspect, the second clutch, the fourth clutch, and the first brake are engaged, or the third clutch, the fourth clutch, By engaging the two brakes, an eighth speed stage having a smaller gear ratio than the seventh speed stage is established.

  According to a twenty-sixth aspect of the invention for achieving the above object, in any one of the twenty-first to twenty-fifth aspects, the reverse gear is established by engaging the fourth clutch, the fifth clutch, and the fourth brake. It is made to be made to be made.

  According to a twenty-seventh aspect of the present invention for achieving the above object, in any one of the first to twenty-sixth aspects, the output of the engine is input to the input rotating member via a fluid transmission device. To do.

  According to the first to twenty-seventh aspects, the first planetary gear device, the second planetary gear device, the third planetary gear device, and the fourth planetary gear device can increase the gear ratio range and the gear ratio step. In addition, a planetary gear type multi-stage transmission for a vehicle that can achieve a suitable forward speed of 7 or more can be obtained.

  In the fourth invention, the eleventh invention, the nineteenth invention, and the twenty-fifth invention, a small planetary gear type multi-speed transmission for a vehicle that can take a large transmission gear ratio range and can make a forward gear ratio with an appropriate transmission gear ratio step. A machine is obtained.

  Further, in the fifth, twelfth, twentieth and twenty-sixth inventions, in addition to the forward speed of 7 or more speeds or the forward speed of 8 speeds, a reverse gear stage of one reverse speed is obtained.

  Further, according to the twenty-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, the second planetary gear device 20, the third planetary gear device 22, the fourth planetary gear device 24, and the output shaft 26 are provided concentrically. 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 same applies to each of the following embodiments.

The first planetary gear unit 18 is a double pinion type planetary gear unit, and includes a first sun gear S1, a plurality of pairs of first planetary gears P1 that mesh with each other, and a first planetary gear P1 that supports the first planetary gear P1 so as to rotate and revolve. A first ring gear R1 meshing with the first sun gear S1 via the carrier CA1 and the first planetary gear P1 is provided, and a predetermined gear ratio ρ ₁ (= number of teeth Z of the first sun gear S1, for example, about “0.491”) is provided. _S1 / the number of teeth Z _R1 of the first ring gear _R1 ).

The second planetary gear unit 20 is also a double pinion type planetary gear unit, and includes a second sun gear S2, a plurality of pairs of second planetary gears P2 that mesh with each other, and a second carrier that supports the second planetary gears P2 so that they can rotate and revolve. A second ring gear R2 meshing with the second sun gear S2 via the CA2 and the second planetary gear P2 is provided, for example, a predetermined gear ratio ρ ₂ of about “0.418” (= the number of teeth Z _S2 of the second sun gear _S2). / The number of teeth Z _R2 ) of the second ring gear R2.

The third planetary gear unit 22 is a single pinion type planetary gear unit, and includes a third sun gear S3, a third planetary gear P3, a third carrier CA3 that supports the third planetary gear P3 so as to rotate and revolve, and a third planetary gear. A third ring gear R3 that meshes with the third sun gear S3 via the gear P3 is provided. For example, a predetermined gear ratio ρ ₃ of about “0.306” (= the number of teeth Z _{S3 of} the third sun gear _S3 / the third ring gear R3) The number of teeth Z _R3 ).

The fourth planetary gear unit 24 is also a single pinion type planetary gear unit, and includes a fourth sun gear S4, a fourth planetary gear P4, a fourth carrier CA4 that supports the fourth planetary gear P4 so that it can rotate and revolve, and a fourth planetary gear. A fourth ring gear R4 that meshes with the fourth sun gear S4 via the gear P4 is provided. For example, a predetermined gear ratio ρ ₄ of about “0.470” (= number of teeth of the fourth sun gear S4 Z _S4 / fourth ring gear R4) The number of teeth Z _R4 ).

  Next, the connection relationship of each component of the first to fourth planetary gear devices 18, 20, 22, and 24 will be described. The first sun gear S1 is selectively connected to the input shaft 16 via the second clutch C2 and is selectively connected to the transmission case 12 via the fourth brake B4. The first carrier CA1 and the second sun gear S2 are integrally connected to each other, selectively connected to the input shaft 16 via the fourth clutch C4, and selected to the transmission case 12 via the first brake B1. Connected. The first ring gear R1, the second ring gear R2, and the third ring gear R3 are integrally connected to each other and selectively connected to the transmission case 12 via the second brake B2. The second carrier CA2 is selectively coupled to the third carrier CA3 via the third clutch C3. The third carrier CA3 is integrally connected to the fourth ring gear R4 and is selectively connected to the transmission case 12 via the third brake B3. The third sun gear S3 and the fourth sun gear S4 are integrally connected to each other and selectively connected to the input shaft 16 via the first clutch C1. The fourth carrier CA4 is connected to the output shaft 26.

  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 between the first clutch C1, the third clutch C3, and the fourth brake B4 causes the second carrier CA2 to move between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4. between the third carrier CA3, by between the first sun gear S1 and the transmission casing 12 are connected, respectively, is established first speed ratio [gamma ₁ is the maximum value, for example, "4.704" is It is done. Further, due to the engagement of the first clutch C1 and the third brake B3, there is a space between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, and between the third carrier CA3 and the fourth ring gear R4 and the transmission case 12. By being connected to each other, the _second speed gear stage in which the speed ratio γ2 is smaller than the first speed gear stage, for example, about “3.128” is established. Further, due to the engagement of the first clutch C1 and the second brake B2, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, the second ring gear R2, the third ring gear R3, the fourth ring gear R4 and the transmission case. by between 12 are connected respectively, the third speed ratio [gamma ₃ is smaller, for example, about "2.087" than the second speed position, is established. Further, due to the engagement of the first clutch C1, the third clutch C3 and the first brake B1, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, between the second carrier CA2 and the third carrier CA3. by between the first carrier CA1 and the second sun gear S2 and the transmission case 12 are respectively connected, the gear ratio gamma ₄ is smaller, for example, about "1.646" than the third gear 4 A speed gear is established. Further, due to the engagement of the first clutch C1, the second clutch C2 and the first brake B1, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, between the first sun gear S1 and the input shaft 16, By connecting the first carrier CA1 and the second sun gear S2 to the transmission case 12, the _fifth speed at which the gear ratio γ5 is smaller than the fourth speed gear stage, for example, about “1.361”. A gear stage is established. Further, due to the engagement of the first clutch C1, the second clutch C2, and the third clutch C3, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, between the first sun gear S1 and the input shaft 16, By connecting the second carrier CA2 and the third carrier CA3, respectively, the _sixth speed gear stage in which the gear ratio γ6 is smaller than the fifth speed gear stage, for example, about “1.000” is established. Be made. Further, due to the engagement of the second clutch C2, the third clutch C3 and the first brake B1, between the first sun gear S1 and the input shaft 16, between the second carrier CA2 and the third carrier CA3, and between the first carrier CA1. by are respectively connected between the and the second sun gear S2 and the transmission case 12, thereby establishing the seventh speed ratio [gamma ₇ is smaller, for example, "0.825" than the sixth-speed position It is done. Further, due to the engagement of the second clutch C2, the third clutch C3 and the second brake B2, between the first sun gear S1 and the input shaft 16, between the second carrier CA2 and the third carrier CA3, the second ring gear R2 by between the third ring gear R3 and the fourth ring gear R4 and the transmission case 12 are respectively connected, the eighth speed gear ratio gamma ₈ is smaller, for example, "0.707" than seventh gear A gear stage is established. In the second speed gear stage and the third speed gear stage, the third clutch C3 may be further engaged.

Further, due to the engagement of the third clutch C3, the fourth clutch C4 and the fourth brake B4, between the second carrier CA2 and the third carrier CA3 and between the first carrier CA1 and the second sun gear S2 and the input shaft 16. by between the first sun gear S1 and the transmission casing 12 are connected, respectively, reverse gear speed ratio gamma _R is slightly larger value, for example, "4.730" than the gear ratio gamma ₁ of the first gear A stage is established. 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 “1.504”. 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 “1.499”, 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 "1.268", 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 "1.288" 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 “1.361”, and the ratio (= γ ₆ / γ ₇ ) between the speed ratio γ ₆ of the _sixth speed gear stage and the speed ratio γ ₇ of the seventh speed gear stage is set to “1.211”. 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 "1.168", the gear ratio gamma is geometric series varied. 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 “6.658”.

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 diagram of FIG. 3 is a two-dimensional coordinate indicating 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 lower horizontal line X1 of these horizontal lines indicates the rotational speed zero, and the upper horizontal line X2 indicates the rotational speed “1.0”, that is, the rotational speed of the input shaft 16. The vertical lines Y1 to Y6 represent the first rotation element RE1 to the sixth rotation element RE6 in order from the left, and the first rotation element RE1 is connected to the first carrier CA1 and the second sun gear S2. The second rotating element RE2 is a first ring gear R1, a second ring gear R2, and a third ring gear R3 that are connected to each other, and the third rotating element RE3 is a third carrier CA3 and a fourth carrier that are connected to each other. Ring gear R4 and second carrier CA2 that is selectively connected to third carrier CA3 and fourth ring gear R4 via third clutch C3. Third carrier CA3 and fourth ring gear R4 are relatively connected in the power transmission path. Function as an output side rotation element RE3out on the output shaft 26 side, and the second carrier CA2 is relatively input shaft in the power transmission path. Functions as an input side rotary element RE3in a 2 side. The fourth rotation element RE4 is the first sun gear S1, the fifth rotation element RE5 is the fourth carrier CA4, and the sixth rotation element RE6 is the third sun gear S3 and the fourth sun gear S4 that are connected to each other. The intervals between the vertical lines Y1 to Y6 are determined according to the gear ratios ρ ₁ , ρ ₂ , ρ ₃ , and ρ ₄ of the first to fourth planetary gear devices 18, 20, 22, and 24, respectively. The vertical axis interval in the figure is determined so that if the distance between the sun gear and the carrier is “1”, the distance between the carrier and the ring gear is ρ.

  If expressed using the collinear diagram, in the transmission 10 of this embodiment, the first rotating element RE1 (CA1, S2) is selectively coupled to the input shaft 16 via the fourth clutch C4. The second rotating element RE2 (R1, R2, R3) is selectively connected to the transmission case 12 via the second brake B2, and is selectively connected to the transmission case 12 via the first brake B1. The third rotating element RE3 (CA2, CA3, R4) is selectively connected to the transmission case 12 via a third brake B3, and the fourth rotating element RE4 (S1) is input to the input shaft via a second clutch C2. 16 and selectively connected to the transmission case 12 via the fourth brake B4, and the fifth rotating element RE5 (CA4 Is connected to the output shaft (Output rotary member) 26, the sixth rotary element RE6 (S3, S4) is configured to be selectively coupled to the input shaft 16 via the first clutch C1.

  Each transmission gear stage will be described based on the alignment chart of FIG. In the first speed gear stage, the first clutch C1 is engaged in a state where the third clutch C3 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are rotated together. As a result, the sixth rotation element RE6 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the fourth brake B4 causes the fourth rotation element RE4 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotation speed, that is, the output of the fifth rotation element RE5 is determined by the point (1st) 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 Y4 and the horizontal line X1 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the second speed gear stage, the sixth rotating element RE6 is connected to the input shaft 16 by the engagement of the first clutch C1 so that the rotation speed is "1", and the third brake element B3 is engaged by the engagement of the third brake B3. At least the output-side rotation element RE3out (CA3, R4) is connected to the transmission case 12 so that the rotation speed is “0”, so that the intersection of the vertical line Y6 and the horizontal line X2 and the vertical line Y3 and the horizontal line X1 The rotation speed of the fifth rotation element RE5, that is, the rotation speed of the output shaft 26 is indicated by the point (2nd) at which the straight line connecting the intersection points intersects the vertical line Y5. In the second gear, the third clutch C3 may be engaged in addition to the first clutch C1 and the third brake B3.

  In the third gear, the sixth rotating element RE6 is connected to the input shaft 16 by the engagement of the first clutch C1, and is set to the rotation speed “1”, and the second rotating element RE2 is engaged by the engagement of the second brake B2. Since it is connected to the transmission case 12 and has a rotational speed of “0”, a straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the intersection of the vertical line Y2 and the horizontal line X1 intersects the vertical line Y5 ( 3rd) indicates the rotation speed of the fifth rotation element RE5, that is, the rotation speed of the output shaft 26. In the third gear, the third clutch C3 may be engaged in addition to the first clutch C1 and the second brake B2.

  In the fourth speed gear stage, the engagement of the first clutch C1 is performed in a state where the third clutch C3 is engaged and the input-side rotation element RE3in and the output-side rotation element RE3out of the third rotation element RE3 are integrally rotated. As a result, the sixth rotation element RE6 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the first brake B1 causes the first rotation element RE1 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotational speed, that is, the output of the fifth rotation element RE5 is determined by the point (4th) 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 Y1 and the horizontal line X1 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the fifth gear, the fourth rotating element RE4 is connected to the input shaft 16 by the engagement of the second clutch C2, and is set to the rotation speed “1”, and the first rotating element RE1 is engaged by the engagement of the first brake B1. Since it is connected to the transmission case 12 and has a rotational speed of “0”, the rotational speed of the second rotational element RE2 connects the intersection of the vertical line Y1 and the horizontal line X1 and the intersection of the vertical line Y4 and the horizontal line X2. A straight line is indicated by a point a intersecting the vertical line Y2. Further, since the sixth rotating element RE6 is connected to the input shaft 16 and has a rotational speed “1” by the engagement of the first clutch C1, a straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the point a. The point (5th) at which Y intersects the vertical line Y5 indicates the rotation speed of the fifth rotation element RE5, that is, the rotation speed of the output shaft 26.

  In the sixth speed, the first clutch C1 is engaged when the third clutch C3 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are rotated together. As a result, the sixth rotation element RE6 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the second clutch C2 causes the fourth rotation element RE4 to be connected to the input shaft 16 so that the rotation speed is “1”. Therefore, the rotational speed, that is, the output of the fifth rotation element RE5 is determined 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 Y4 and the horizontal line X2 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the seventh speed, the second clutch C2 is engaged in a state where the third clutch C3 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are rotated together. As a result, the fourth rotation element RE4 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the first brake B1 causes the first rotation element RE1 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotation speed, that is, the output of the fifth rotation element RE5 is determined by the point (7th) at which the straight line connecting the intersection of the vertical line Y4 and the horizontal line X2 and the intersection of the vertical line Y1 and the horizontal line X1 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the eighth speed, the second clutch C2 is engaged when the third clutch C3 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are integrally rotated. As a result, the fourth rotation element RE4 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the second brake B2 causes the second rotation element RE2 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotational speed, that is, the output of the fifth rotation element RE5 is determined by the point (8th) at which the straight line connecting the intersection of the vertical line Y2 and the horizontal line X1 and the intersection of the vertical line Y4 and the horizontal line X2 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the reverse gear, when the third clutch C3 is engaged and the input-side rotation element RE3in and the output-side rotation element RE3out of the third rotation element RE3 are rotated together, the fourth clutch C4 is engaged. The 1-rotation element RE1 is connected to the input shaft 16 so as to have a rotation speed “1”, and the engagement of the fourth brake B4 causes the fourth rotation element RE4 to be connected to the transmission case 12 so that the rotation speed is “0”. A negative rotation speed of the output shaft 26 is indicated by a point (Rev) where a straight line connecting the intersection of the vertical line Y1 and the horizontal line X2 and the intersection of the vertical line Y4 and the horizontal line X1 intersects the vertical line Y5.

  As described above, according to this embodiment, the four planetary gear units 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 can change the transmission ratio. A vehicular planetary gear type multi-stage transmission capable of a large forward 7th speed or more is obtained.

Further, in the present embodiment, the third rotation of the six rotation elements constituted by connecting part of the sun gear, the carrier, and the ring gear of the four sets of planetary gear devices 18, 20, 22, and 24 to each other. The element is composed of an input side rotation element REin (CA2) and an output side rotation element RE3out (CA3, R4) selectively connected to each other by the third clutch C3, and the third clutch C3 is released. Since the fifth gear stage is established, a planetary gear type multi-stage transmission for a vehicle is obtained in which, in addition to a large gear ratio range, the gear ratio step is also capable of an appropriate forward eight speed. 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, “6.658”, for example, the vehicle planetary gear type multi-stage transmission 10 that can achieve both high speed running and uphill starting performance can be obtained.

  In addition, according to the present embodiment, the reverse shift stage is established by engaging the third clutch C3, the fourth clutch C4, and the fourth brake B4. Therefore, in addition to the eighth forward speed, A transmission gear stage is obtained.

  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 30 according to the second embodiment of the present invention, and FIG. The second embodiment is
The gear ratio ρ _{2 of} the second planetary gear device 32 and the members to which the components of the second planetary gear device 32 are connected are different from those of the first embodiment described above, but other configurations and engagement operations are the same. This is similar to the first embodiment, and the same effect as the first embodiment can be obtained. Below, the different part is demonstrated.

The second planetary gear device 32 of the second embodiment includes 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. Te is a double-pinion type planetary gear device provided with a second ring gear R2 meshing with second sun gear S2, for example, it has a gear ratio [rho ₂ of about "0.582".

  The second sun gear S2 is selectively connected to the third carrier CA3 via the third clutch C3, and the second carrier CA2 is integrally connected to the first carrier CA1. Further, the second ring gear R2 is integrally connected to the first ring gear R1 and the third ring gear R3 as in the first embodiment.

In the transmission 30 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 _18, the gear ratio [rho ₂ of the second planetary gear _32, 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 collinear diagram of FIG. 5, the first rotating element RE1 includes a first carrier CA1 and a second carrier CA2, and the input-side rotating element RE3in of the third rotating element RE3 includes a second sun gear S2. Other rotating elements RE are the same as those in the first embodiment. Based on this rotating element, the alignment chart shown in FIG. 5 differs from the alignment chart shown in FIG. 3 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 for explaining the configuration of the transmission 40 of the third embodiment. FIG. 7 shows the operation of the hydraulic friction engagement device necessary for establishing each transmission gear stage in the transmission 40. FIG. 8 is a collinear diagram showing the rotational speed of the rotating element at each gear stage.

  The third embodiment is different from the first embodiment in that it has five clutches C1 to C5, and since it has five clutches C1 to C5, the engagement operation is also the first embodiment. Is different. The other configuration is the same as that of the first embodiment, and has four sets of planetary gear devices 18, 20, 22, 24 similar to those of the first embodiment, and the four sets of planetary gear devices 18, The connection relationship between the constituent elements 20, 22, and 24 is the same as that in the first embodiment. A member having brakes B1 to B4 and selectively connected to the transmission case 12 by the brakes B1 to B4 is the same as that of the first embodiment. Hereinafter, a description will be given focusing on the differences from the first embodiment.

  The first clutch C1 selectively connects between the third sun gear S3 and the fourth sun gear S4 and the input shaft 16, and the second clutch C2 selectively connects between the second carrier CA2 and the input shaft 16. The third clutch C3 selectively connects between the first sun gear S1 and the input shaft 16, and the fourth clutch C4 selectively connects between the second carrier CA2 and the third carrier CA3. The fifth clutch C5 selectively connects the first carrier CA1, the second sun gear S2, and the input shaft 16.

In the transmission 40 configured as described above, for example, as shown in the engagement operation table of FIG. 7, two to three selected from the clutches C1 to C5 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. 7, the engagement of the first clutch C1, the fourth clutch C4, and the fourth brake B4 causes the second carrier CA2 to move between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4. between the third carrier CA3, by between the first sun gear S1 and the transmission casing 12 are connected, respectively, first gear speed ratio gamma ₁ is located at a maximum value, for example "4.704" degree Is established. Further, due to the engagement of the first clutch C1 and the third brake B3, there is a space between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, and between the third carrier CA3 and the fourth ring gear R4 and the transmission case 12. By being connected to each other, the _second speed gear stage in which the speed ratio γ2 is smaller than the first speed gear stage, for example, about “3.128” is established. Further, due to the engagement of the first clutch C1 and the second brake B2, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, the second ring gear R2, the third ring gear R3, the fourth ring gear R4 and the transmission case. The _third speed gear stage in which the speed ratio γ3 is smaller than the second speed gear stage, for example, about “2.087”, is established. Further, due to the engagement of the first clutch C1, the fourth clutch C4 and the first brake B1, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, between the second carrier CA2 and the third carrier CA3. by between the first carrier CA1 and the second sun gear S2 and the transmission case 12 are respectively connected, the gear ratio gamma ₄ is smaller, for example, about "1.646" than the third gear 4 A speed gear is established. Further, due to the engagement of the first clutch C1, the second clutch C2 and the first brake B1, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, between the first sun gear S1 and the input shaft 16, By connecting the first carrier CA1 and the second sun gear S2 and the transmission case 12 to each other, the _fifth speed in which the gear ratio γ5 is smaller than the fourth speed gear stage, for example, about “1.278”. A gear stage is established. Further, due to the engagement of the first clutch C1, the second clutch C2, and the fourth clutch C4, between the input shaft 16 and the third sun gear S3 and the fourth sun gear S4, between the first sun gear S1 and the input shaft 16, By connecting the second carrier CA2 and the third carrier CA3, respectively, the _sixth speed gear stage in which the gear ratio γ6 is smaller than the fifth speed gear stage, for example, about “1.000” is established. Be made. Further, due to the engagement of the third clutch C3, the fourth clutch C4, and the first brake B1, between the first sun gear S1 and the input shaft 16, between the second carrier CA2 and the third carrier CA3, and between the first carrier CA1. by are respectively connected between the and the second sun gear S2 and the transmission case 12, thereby establishing the seventh speed ratio [gamma ₇ is smaller, for example, "0.825" than the sixth-speed position It is done. In the second speed gear stage and the third speed gear stage, the fourth clutch C4 may be further engaged. Further, when shifting from the fifth gear to the seventh gear through the sixth gear, the number of friction engagement devices to be controlled to establish the seventh gear is reduced. Therefore, after the sixth gear is established, the third clutch C3 is engaged and the second clutch C2 is released.

Further, the eighth speed gear stage is established by one of the following. That is, by engagement of the second clutch C2, the fourth clutch C4, and the first brake B1, between the first sun gear S1 and the input shaft 16, between the second carrier CA2 and the third carrier CA3, the second ring gear R2 by between the third ring gear R3 and the fourth ring gear R4 and the transmission case 12 are respectively connected, the gear ratio gamma _8-1 is smaller, for example, "0.696" than seventh gear The 8-1 speed gear stage is established, and the engagement of the third clutch C3, the fourth clutch C4, and the second brake B2 causes the second carrier CA2 and the third carrier between the first sun gear S1 and the input shaft 16. The transmission case 12 is connected to the CA3, the second ring gear R2, the third ring gear R3, and the fourth ring gear R4. Accordingly, the 8-2 speed ratio [gamma _8-2 is smaller, for example, "0.707" than the seventh-speed position, is established.

Further, due to the engagement of the fourth clutch C4, the fifth clutch C5 and the fourth brake B4, between the second carrier CA2 and the third carrier CA3 and between the first carrier CA1 and the second sun gear S2 and the input shaft 16. by between the first sun gear S1 and the transmission casing 12 are connected, respectively, reverse gear speed ratio gamma _R is slightly larger value, for example, "4.730" than the gear ratio gamma ₁ of the first gear A stage is established.

In the transmission 40, 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 “1.504”. 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 “1.499”, 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 "1.268", 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 "1.288" 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 “1.278”, and the ratio (= γ ₆ / γ ₇ ) of the speed ratio γ ₆ of the _sixth gear and the speed ratio γ ₇ of the seventh gear is “1.211”. are, gear ratio and the gear ratio gamma ₇ of seventh gear first 8-1 gear speed gamma _8-1 The ratio (= γ ₇ / γ _8-1) is a "1.186", the ratio of the speed ratio gamma _8-2 with the speed ratio gamma ₇ of seventh gear first 8-2 speed gear position ( = Γ ₇ / γ _8-2 ) is set to “1.168”, and the respective transmission gear ratios γ are changed in substantially equal ratios. In the above transmission 40, the eighth speed gear ratio width or first speed ratio range when the gear stage and the first 8-1 gear speed (= gamma ₁ / gamma _8-1) is "6.756" , and the gear ratio width or second gear ratio range in the case where the eighth gear to the first 8-2 gear speed (= γ _{1 /} γ _8-2) is "6.658", and in any Even so, the gear ratio range is a relatively large value.

  FIG. 8 is a collinear diagram that can represent, on a straight line, the relative relationship between the rotational speeds of the rotating elements having different coupling states for each gear stage in the transmission 40. The collinear chart of FIG. 8 shows the relationship of the gear ratio ρ of each planetary gear unit 18, 20, 22, 24 in the horizontal axis direction, and is a two-dimensional coordinate indicating the relative rotational speed in the vertical axis direction. , X2, the meanings of the vertical lines Y1 to Y6, and the specific members meant by the rotating elements RE1 to RE6 are the same as in FIG.

  If expressed using the collinear diagram, in the transmission 40 of this embodiment, the first rotation element RE1 (CA1, S2) is selectively coupled to the input shaft 16 via the fifth clutch C5. The second rotating element RE2 (R1, R2, R3) is selectively connected to the transmission case 12 via the second brake B2, and is selectively connected to the transmission case 12 via the first brake B1. The third rotating element RE3 (CA2, CA3, R4) is selectively connected to the input shaft 16 via the second clutch C2, and is selectively connected to the transmission case 12 via the third brake B3. The fourth rotating element RE4 (S1) is selectively connected to the input shaft 16 via the third clutch C3 and is transmitted via the fourth brake B4. The fifth rotating element RE5 (CA4) is connected to an output shaft (output rotating member) 26, and the sixth rotating element RE6 (S3, S4) is connected via the first clutch C1. It is configured to be selectively connected to the input shaft 16.

  Each transmission gear stage will be described based on the alignment chart of FIG. In the first speed gear stage, the first clutch C1 is engaged in a state where the fourth clutch C4 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are rotated together. As a result, the sixth rotation element RE6 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the fourth brake B4 causes the fourth rotation element RE4 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotation speed, that is, the output of the fifth rotation element RE5 is determined by the point (1st) 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 Y4 and the horizontal line X1 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the second speed gear stage, the sixth rotating element RE6 is connected to the input shaft 16 by the engagement of the first clutch C1 so that the rotation speed is "1", and the third brake element B3 is engaged by the engagement of the third brake B3. At least the output-side rotation element RE3out (CA3, R4) is connected to the transmission case 12 so that the rotation speed is “0”, so that the intersection of the vertical line Y6 and the horizontal line X2 and the vertical line Y3 and the horizontal line X1 The rotation speed of the fifth rotation element RE5, that is, the rotation speed of the output shaft 26 is indicated by the point (2nd) at which the straight line connecting the intersection points intersects the vertical line Y5. In the second gear, the fourth clutch C4 may be engaged in addition to the first clutch C1 and the third brake B3.

  In the third gear, the sixth rotating element RE6 is connected to the input shaft 16 by the engagement of the first clutch C1, and is set to the rotation speed “1”, and the second rotating element RE2 is engaged by the engagement of the second brake B2. Since it is connected to the transmission case 12 and has a rotational speed of “0”, a straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the intersection of the vertical line Y2 and the horizontal line X1 intersects the vertical line Y5 ( 3rd) indicates the rotation speed of the fifth rotation element RE5, that is, the rotation speed of the output shaft 26. In the third gear, the fourth clutch C4 may be engaged in addition to the first clutch C1 and the second brake B2.

  In the fourth speed gear stage, the engagement of the first clutch C1 is performed in a state in which the fourth clutch C4 is engaged and the input-side rotation element RE3in and the output-side rotation element RE3out of the third rotation element RE3 are integrally rotated. As a result, the sixth rotation element RE6 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the first brake B1 causes the first rotation element RE1 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotational speed, that is, the output of the fifth rotation element RE5 is determined by the point (4th) 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 Y1 and the horizontal line X1 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the fifth speed gear stage, the third rotating element RE3 is connected to the input shaft 16 by the engagement of the second clutch C2, and the rotation speed is "1", and the first rotating element RE1 is engaged by the engagement of the first brake B1. Since it is connected to the transmission case 12 and has a rotational speed “0”, the rotational speed of the second rotational element RE2 connects the intersection of the vertical line Y1 and the horizontal line X1 and the intersection of the vertical line Y3 and the horizontal line X2. A straight line is indicated by a point a intersecting the vertical line Y2. Further, since the sixth rotating element RE6 is connected to the input shaft 16 and has a rotational speed “1” by the engagement of the first clutch C1, a straight line connecting the intersection of the vertical line Y6 and the horizontal line X2 and the point a. The point (5th) at which Y intersects the vertical line Y5 indicates the rotation speed of the fifth rotation element RE5, that is, the rotation speed of the output shaft 26.

  In the sixth speed, the first clutch C1 is engaged in a state where the fourth clutch C4 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are integrally rotated. As a result, the sixth rotation element RE6 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the second clutch C2 causes the third rotation element RE3 to be connected to the input shaft 16 so that the rotation speed is “1”. Therefore, the rotational speed, that is, the output of the fifth rotation element RE5 is determined 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 Y4 and the horizontal line X2 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the seventh speed, the fourth clutch C4 is engaged, and the third clutch C3 is engaged in a state where the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are integrally rotated. As a result, the fourth rotation element RE4 is connected to the input shaft 16 so that the rotation speed is “1”, and the engagement of the first brake B1 causes the first rotation element RE1 to be connected to the transmission case 12 so that the rotation speed is “0”. Therefore, the rotation speed, that is, the output of the fifth rotation element RE5 is determined by the point (7th) at which the straight line connecting the intersection of the vertical line Y4 and the horizontal line X2 and the intersection of the vertical line Y1 and the horizontal line X1 intersects the vertical line Y5. The rotational speed of the shaft 26 is shown.

  In the eighth-first gear, the fourth clutch C4 is engaged, and the input side rotating element RE3in and the output side rotating element RE3out of the third rotating element RE3 are integrally rotated. Due to the engagement, the third rotation element RE3 is connected to the input shaft 16 so that the rotation speed is “1”, and by engagement of the first brake B1, the first rotation element RE1 is connected to the transmission case 12 and the rotation speed is “0”. Therefore, a point connecting the intersection of the vertical line Y1 and the horizontal line X1 and the intersection of the vertical line Y3 and the horizontal line X2 intersects the vertical line Y5 (8th-1), so that the fifth rotation element RE5 The rotational speed, that is, the rotational speed of the output shaft 26 is shown.

  In the eighth to second gear, the fourth clutch C4 is engaged, and the input side rotating element RE3in and the output side rotating element RE3out of the third rotating element RE3 are integrally rotated. Due to the engagement, the fourth rotation element RE4 is connected to the input shaft 16 so that the rotation speed is “1”, and by the engagement of the second brake B2, the second rotation element RE2 is connected to the transmission case 12 and the rotation speed is “0”. Therefore, a point connecting the intersection of the vertical line Y2 and the horizontal line X1 and the intersection of the vertical line Y4 and the horizontal line X2 intersects the vertical line Y5 (8th-2). The rotational speed, that is, the rotational speed of the output shaft 26 is shown.

  In the reverse gear, when the fourth clutch C4 is engaged and the input-side rotating element RE3in and the output-side rotating element RE3out of the third rotating element RE3 are integrally rotated, the fifth clutch C5 is engaged. The 1-rotation element RE1 is connected to the input shaft 16 so as to have a rotation speed “1”, and the engagement of the fourth brake B4 causes the fourth rotation element RE4 to be connected to the transmission case 12 so that the rotation speed is “0”. A negative rotation speed of the output shaft 26 is indicated by a point (Rev) where a straight line connecting the intersection of the vertical line Y1 and the horizontal line X2 and the intersection of the vertical line Y4 and the horizontal line X1 intersects the vertical line Y5.

  As described above, according to this embodiment, the four planetary gear units 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 can change the transmission ratio. A vehicular planetary gear type multi-stage transmission capable of a large forward 7th speed or more is obtained.

Further, in the present embodiment, the third rotation of the six rotation elements constituted by connecting part of the sun gear, the carrier, and the ring gear of the four sets of planetary gear devices 18, 20, 22, and 24 to each other. The element is composed of an input side rotation element REin (CA2) and an output side rotation element RE3out (CA3, R4) selectively connected to each other by the fourth clutch C4, and the fourth clutch C4 is released. Since the fifth gear stage is established, a planetary gear type multi-stage transmission for a vehicle is obtained in which, in addition to a large gear ratio range, the gear ratio step is also capable of an appropriate forward eight speed. That is, the respective gear ratios γ are changed in a substantially equal ratio to obtain excellent speed increasing characteristics or acceleration characteristics by changing gear positions, and the gear ratio width of the transmission 40 (= γ ₁ / γ _8-1). or γ _{1 /} γ _8-2) because there is a relatively large value, for example, "6.756 or 6.658", for example, high-speed running and uphill start performance and are compatible vehicular planetary gear type step-variable transmission 40 Is obtained.

  Also in this embodiment, in addition to the eighth forward speed, a reverse gear stage is obtained. 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 are sequentially arranged between the input shaft 16 and the output shaft 26, and the output of the engine 8 is Since it is inputted to the input shaft 16 of the transmission 40 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 fourth embodiment of the present invention will be described. FIG. 9 is a skeleton diagram illustrating the configuration of the transmission 50 of the fourth embodiment, and FIG. 10 is a collinear diagram showing the rotational speeds of the rotating elements at each gear stage. The fourth embodiment is different from the second embodiment in that it has five clutches C1 to C5, but has four sets of planetary gear units 18, 32, 22, and 24 similar to the second embodiment. In addition, the connection relationship among the components of the four sets of planetary gear devices 18, 32, 22, 24 is the same as that of the second embodiment. A member having brakes B1 to B4 and selectively connected to the transmission case 12 by the brakes B1 to B4 is the same as that of the second embodiment.

  In the fourth embodiment, the first clutch C1 selectively connects the third sun gear S3 and the fourth sun gear S4 and the input shaft 16, and the second clutch C2 includes the second sun gear S2 and the input shaft 16. The third clutch C3 selectively connects the first sun gear S1 and the input shaft 16, and the fourth clutch C4 is connected between the second sun gear S2 and the third carrier CA3. The fifth clutch C5 selectively connects the first carrier CA1 and the second carrier CA2 and the input shaft 16 with each other.

In the transmission 50 configured as described above, similarly to the third 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 third embodiment is obtained for each gear stage. The gear ratio [rho ₁ of the first planetary gear unit _18, the gear ratio [rho ₂ of the second planetary gear _32, 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 collinear diagram of FIG. 10, the first rotation element RE1 includes a first carrier CA1 and a second carrier CA2, and the input side rotation element RE3in of the third rotation element RE3 includes a second sun gear S2. Other rotating elements RE are the same as those in the third embodiment. Based on this rotating element, the collinear diagram shown in FIG. 10 differs from the collinear diagram shown in FIG. 8 only in the configuration of each rotating element, and is the same as the collinear diagram. The explanation of the alignment chart of FIG. 10 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, 30, 40, and 50 of the above-described embodiments, the forward eight-speed gear stage is established, but except for any one of the eight-speed gear stages, the forward seventh speed is established. May be established.

  In the transmissions 10, 30, 40, and 50 of the above-described embodiments, the engine 8 and the torque converter 14 are directly connected via the crankshaft 9, but are operatively connected via, for example, a gear, a belt, or the like. It is only necessary to be arranged, and it is not necessary to arrange them on a common axis. The engine 8 may be another driving force source such as an electric motor.

  In the transmissions 10, 30, 40, and 50 of the above-described embodiments, a one-way clutch may be provided in series or in parallel with at least one of the clutches C1 to C5 and the brakes B1 to B4. In this way, shift control becomes easy. Further, at least one of the clutches C1 to C5 and the brakes B1 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 alignment chart of the above-described embodiment, the vertical lines Y1 to Y6 are sequentially arranged from the left to the right. However, the vertical lines Y1 to Y6 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.

  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 a table | surface which shows the relationship between the transmission gear stage of the planetary gear type multistage transmission for vehicles of 3rd Example, and the action | operation of the hydraulic frictional engagement apparatus required in order to establish it. 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.

Explanation of symbols

8: Engine 10, 30, 40, 50: 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)
26: Output shaft (output rotating member)
18: First planetary gear unit 20: Second planetary gear unit 22: Third planetary gear unit 24: Fourth planetary gear unit 32: Second planetary gear unit

Claims (27)

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 the ring gear of the first planetary gear device to the fourth planetary gear device are connected to each other to constitute six rotating elements, and the rotational speeds of the six rotating elements are linearly adjusted. In the nomographic chart that can be represented, the six rotation elements are sequentially arranged from one end to the other end in the order of a first rotation element, a second rotation element, a third rotation element, a fourth rotation element, a fifth rotation element, and When the sixth rotating element is used, the first rotating element is selectively connected to the input rotating member via the fourth clutch and 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, the third rotating element is selectively connected to the non-rotating member via the third brake, and the first rotating element and The second rotating element An input-side rotation element whose rotation is uniquely determined from the rotation, and an output-side rotation element whose rotation is uniquely determined from the rotation of the second rotation element and the sixth rotation element, the input-side rotation element and the output The side rotation elements are selectively connected to each other via a third clutch to be integrally rotated, and the fourth rotation element is selectively connected to the input rotation member via a second clutch and is The fifth rotary element is selectively connected to the output rotary member via the four brakes, the sixth rotary element is selectively connected to the input rotary member via the first clutch. And
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake. The planetary gear type multi-stage transmission for a vehicle according to claim 1,
The vehicle is characterized in that at least a seventh forward speed is established by selectively switching between engagement and disengagement states of the first to third clutches and the first to fourth brakes. Planetary gear type multi-stage transmission. The vehicular planetary gear type multi-stage transmission according to claim 2,
When the first clutch, the third clutch, and the fourth brake are engaged, the first gear stage having the largest gear ratio is established, and the first clutch 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 the gear ratio is smaller than that of the second gear stage by engaging the first clutch and the second brake. A gear stage is established, and the first clutch, the third clutch, and the first brake are engaged to establish a fourth gear stage having a smaller gear ratio than the third gear stage. By engaging the first clutch, the second clutch, and the first brake, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established. By engaging the first clutch, the second clutch, and the third clutch, a sixth shift stage having a gear ratio smaller than the fifth shift stage is established, and the second clutch, the third clutch A planetary gear type multi-stage transmission for a vehicle, wherein a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established by engaging the first brake. The vehicular planetary gear type multi-stage transmission according to claim 3,
A planetary gear type multi-stage for a vehicle characterized in that an eighth speed having a gear ratio smaller than that of the seventh speed is established by engaging the second clutch, the third clutch, and the second brake. transmission. A vehicular planetary gear type multi-stage transmission according to any one of claims 1 to 4,
A planetary gear type multi-stage transmission for a vehicle, wherein the reverse gear is established by engaging the third clutch, the fourth clutch, and the fourth brake. The vehicular planetary gear type multi-stage transmission according to any one of claims 1 to 5,
The first planetary gear 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 is a double pinion type planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planet gears rotatably supported by the second carrier. ,
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.
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 first rotating element is the first carrier and the second sun gear, the second rotating element is the first ring gear, the second ring gear and the third ring gear, and the input side rotation of the third rotating element The element is the second carrier, the output side rotating element of the third rotating element is the third carrier and the fourth ring gear, the fourth rotating element is the first sun gear, and the fifth rotating element Is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear. The vehicular planetary gear type multi-stage transmission according to any one of claims 1 to 5,
The first planetary gear 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 is a double pinion type planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planet gears rotatably supported by the second carrier. ,
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.
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 first rotating element is the first carrier and the second carrier, the second rotating element is the first ring gear, the second ring gear, and the third ring gear, and the input side rotation of the third rotating element The element is the second sun gear, the output side rotating element of the third rotating element is the third carrier and the fourth ring gear, the fourth rotating element is the first sun gear, and the fifth rotating element Is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear. 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 the ring gear of the first planetary gear device to the fourth planetary gear device are connected to each other to constitute six rotating elements, and the rotational speeds of the six rotating elements are linearly adjusted. In the nomographic chart that can be represented, the six rotation elements are sequentially arranged from one end to the other end in the order of a first rotation element, a second rotation element, a third rotation element, a fourth rotation element, a fifth rotation element, and When the sixth rotating element is used, the first rotating element is selectively connected to the input rotating member via the fifth clutch and is selectively connected to the non-rotating member via the first brake. The two-rotating element is selectively connected to the non-rotating member via the second brake, and the third rotating element is selectively connected to the input rotating member via the second clutch and via the third brake. Non-rotating member An input-side rotating element that is selectively connected and the third rotating element is uniquely determined from the rotation of the first rotating element and the second rotating element, the second rotating element, and the sixth rotating element An output-side rotation element whose rotation is uniquely determined from the rotation of the element, and the input-side rotation element and the output-side rotation element are selectively connected to each other via a fourth clutch to be integrally rotated. The fourth rotating element is selectively connected to the input rotating member via a third clutch and is selectively connected to a non-rotating member via a fourth brake, and the fifth rotating element is connected to the output rotation. Connected to a member, the sixth rotating element is selectively connected to the input rotating member via a first clutch,
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake. The vehicular planetary gear type multi-stage transmission according to claim 8,
The vehicle is characterized in that at least a forward seventh speed is established by selectively switching between engagement and disengagement states of the first to fourth clutches and the first to fourth brakes. Planetary gear type multi-stage transmission. The planetary gear type multi-stage transmission for a vehicle according to claim 9,
When the first clutch, the fourth clutch, and the fourth brake are engaged, the first gear stage having the largest gear ratio is established, and the first clutch 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 the gear ratio is smaller than that of the second gear stage by engaging the first clutch and the second brake. A gear stage is established, and the first clutch, the fourth 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. By engaging the first clutch, the second clutch, and the first brake, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established. By engaging the first clutch, 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 clutch, the fourth clutch A planetary gear type multi-stage transmission for a vehicle, wherein a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established by engaging the first brake. The vehicle planetary gear type multi-stage transmission according to claim 10,
When the second clutch, the fourth clutch, and the first brake are engaged, or when the third clutch, the fourth clutch, and the second brake are engaged, than the seventh gear. A planetary gear type multi-stage transmission for a vehicle, characterized in that an eighth speed with a small speed ratio is established. A planetary gear type multi-stage transmission for a vehicle according to any one of claims 8 to 11,
A planetary gear type multi-stage transmission for a vehicle, wherein a reverse gear is established by engaging the fourth clutch, the fifth clutch, and the fourth brake. A vehicular planetary gear type multi-stage transmission according to any one of claims 8 to 12,
The first planetary gear 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 is a double pinion type planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planet gears rotatably supported by the second carrier. ,
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.
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 first rotating element is the first carrier and the second sun gear, the second rotating element is the first ring gear, the second ring gear and the third ring gear, and the input side rotation of the third rotating element The element is the second carrier, the output side rotating element of the third rotating element is the third carrier and the fourth ring gear, the fourth rotating element is the first sun gear, and the fifth rotating element Is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear. A vehicular planetary gear type multi-stage transmission according to any one of claims 8 to 12,
The first planetary gear 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 is a double pinion type planetary gear device including a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planet gears rotatably supported by the second carrier. ,
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.
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 first rotating element is the first carrier and the second carrier, the second rotating element is the first ring gear, the second ring gear, and the third ring gear, and the input side rotation of the third rotating element The element is the second sun gear, the output side rotating element of the third rotating element is the third carrier and the fourth ring gear, the fourth rotating element is the first sun gear, and the fifth rotating element Is the fourth carrier, and the sixth rotating element is the third sun gear and the fourth sun gear. 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 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 double pinion type second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier;
A single pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear;
Including a fourth sun gear, a fourth carrier, and a single pinion type fourth planetary gear device provided with a fourth ring gear;
The first carrier and the second sun gear are selectively connected to the input rotating member via a fourth clutch and selectively connected to a non-rotating member via a first brake, and the first ring gear, The second ring gear and the third ring gear are selectively connected to a non-rotating member via a second brake, and the second carrier and the third carrier are selectively connected to each other via a third clutch, The third carrier and the fourth ring gear are selectively connected to a non-rotating member via a third brake, and the first sun gear is selectively connected to the input rotating member via a second clutch and The fourth carrier is connected to the output rotating member through a brake and is selectively connected to the non-rotating member. The third sun gear and the fourth sun gear are connected to the input rotation through a first clutch. It is selectively connected to the timber,
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake. 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 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 double pinion type second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier;
A single pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear;
Including a fourth sun gear, a fourth carrier, and a single pinion type fourth planetary gear device provided with a fourth ring gear;
The first carrier and the second carrier are selectively connected to the input rotating member via a fourth clutch and selectively connected to a non-rotating member via a first brake, and the first ring gear, The second ring gear and the third ring gear are selectively connected to a non-rotating member via a second brake, and the second sun gear and the third carrier are selectively connected to each other via a third clutch, The third carrier and the fourth ring gear are selectively connected to a non-rotating member via a third brake, and the first sun gear is selectively connected to the input rotating member via a second clutch and The fourth carrier is connected to the output rotating member through a brake and is selectively connected to the non-rotating member. The third sun gear and the fourth sun gear are connected to the input rotation through a first clutch. It is selectively connected to the timber,
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake. The planetary gear type multi-stage transmission for a vehicle according to claim 15 or 16,
The vehicle is characterized in that at least a seventh forward speed is established by selectively switching between engagement and disengagement states of the first to third clutches and the first to fourth brakes. Planetary gear type multi-stage transmission. The planetary gear type multi-stage transmission for a vehicle according to claim 17,
When the first clutch, the third clutch, and the fourth brake are engaged, the first gear stage having the largest gear ratio is established, and the first clutch 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 the gear ratio is smaller than that of the second gear stage by engaging the first clutch and the second brake. A gear stage is established, and the first clutch, the third clutch, and the first brake are engaged to establish a fourth gear stage having a smaller gear ratio than the third gear stage. By engaging the first clutch, the second clutch, and the first brake, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established. By engaging the first clutch, the second clutch, and the third clutch, a sixth shift stage having a gear ratio smaller than the fifth shift stage is established, and the second clutch, the third clutch A planetary gear type multi-stage transmission for a vehicle, wherein a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established by engaging the first brake. The planetary gear type multi-stage transmission for a vehicle according to claim 18,
A planetary gear type multi-stage for a vehicle characterized in that an eighth speed having a gear ratio smaller than that of the seventh speed is established by engaging the second clutch, the third clutch, and the second brake. transmission. A planetary gear type multi-stage transmission for a vehicle according to any one of claims 15 to 19,
A planetary gear type multi-stage transmission for a vehicle, wherein the reverse gear is established by engaging the third clutch, the fourth clutch, and the fourth brake. 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 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 double pinion type second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier;
A single pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear;
Including a fourth sun gear, a fourth carrier, and a single pinion type fourth planetary gear device provided with a fourth ring gear;
The first carrier and the second sun gear are selectively connected to the input rotating member via a fifth clutch and selectively connected to a non-rotating member via a first brake, and the first ring gear, The second ring gear and the third ring gear are selectively connected to a non-rotating member via a second brake, the second carrier and the third carrier are selectively connected to each other via a fourth clutch; and The second carrier is selectively connected to the input rotating member via a second clutch, and the third carrier and the fourth ring gear are selectively connected to a non-rotating member via a third brake, The first sun gear is selectively connected to the input rotating member via a third clutch and is selectively connected to a non-rotating member via a fourth brake, and the fourth carrier is connected to the output rotating member. Is sintered, said third sun gear and said fourth sun gear are selectively connected to the input rotary member through a first clutch,
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake. 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 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 double pinion type second planetary gear device comprising a second sun gear, a second carrier, and a second ring gear, and having a pair of meshing planetary gears rotatably supported by the second carrier;
A single pinion type third planetary gear device comprising a third sun gear, a third carrier, and a third ring gear;
Including a fourth sun gear, a fourth carrier, and a single pinion type fourth planetary gear device provided with a fourth ring gear;
The first carrier and the second carrier are selectively connected to the input rotating member via a fifth clutch and selectively connected to the non-rotating member via a first brake, and the first ring gear, The second ring gear and the third ring gear are selectively connected to a non-rotating member via a second brake, the second sun gear and the third carrier are selectively connected to each other via a fourth clutch; and , the second sun gear is selectively connected to the input rotary member through a second clutch, the third carrier and the fourth ring gear is selectively connected to the non-rotating member through a third brake, the The first sun gear is selectively connected to the input rotating member via a third clutch and is selectively connected to a non-rotating member via a fourth brake, and the fourth carrier is connected to the output rotating member. Is sintered, said third sun gear and said fourth sun gear are selectively connected to the input rotary member through a first clutch,
A planetary gear type multi-stage transmission for a vehicle, wherein a plurality of shift stages are established by selectively switching between engagement and disengagement states of the clutch and brake.
The planetary gear type multi-stage transmission for a vehicle according to claim 21 or claim 22,
The vehicle is characterized in that at least a forward seventh speed is established by selectively switching between engagement and disengagement states of the first to fourth clutches and the first to fourth brakes. Planetary gear type multi-stage transmission. The planetary gear type multi-stage transmission for a vehicle according to claim 23,
When the first clutch, the fourth clutch, and the fourth brake are engaged, the first gear stage having the largest gear ratio is established, and the first clutch 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 the gear ratio is smaller than that of the second gear stage by engaging the first clutch and the second brake. A gear stage is established, and the first clutch, the fourth 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. By engaging the first clutch, the second clutch, and the first brake, a fifth shift stage having a gear ratio smaller than that of the fourth shift stage is established. By engaging the first clutch, 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 clutch, the fourth clutch A planetary gear type multi-stage transmission for a vehicle, wherein a seventh shift stage having a gear ratio smaller than that of the sixth shift stage is established by engaging the first brake. The planetary gear type multi-stage transmission for a vehicle according to claim 24,
When the second clutch, the fourth clutch, and the first brake are engaged, or when the third clutch, the fourth clutch, and the second brake are engaged, than the seventh gear. A planetary gear type multi-stage transmission for a vehicle, characterized in that an eighth speed with a small gear ratio is established. A planetary gear type multi-stage transmission for a vehicle according to any one of claims 21 to 25,
A planetary gear type multi-stage transmission for a vehicle, wherein a reverse gear is established by engaging the fourth clutch, the fifth clutch, and the fourth brake. A vehicular planetary gear type multi-stage transmission according to any one of claims 1 to 26,
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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