JP2010038333A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission with short shaft length and excellent in engagement transmission efficiency. <P>SOLUTION: The automatic transmission includes two first/second planetary gears 5, 6. A sun gear Sf of the first planetary gear 5 is connected to an input shaft 2. A carrier Cf of the first planetary gear 5 is connected to an output shaft 3 arranged in parallel with the input shaft 2 via a first gear train G1, and a ring gear Rr of the second planetary gear 6 is connected via a second gear train G2. The transmission is equipped with a first engagement element C1 for connecting a sun gear Sr of the second planetary gear 6 and the input shaft 2, a second engagement element C2 for connecting a carrier Cr of the second planetary gear 6 and the input shaft 2, a third engagement element C3 for connecting a ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6, a fourth engagement element B1 for fixing the sun gear Sr of the second planetary gear 6 to a transmission case, and a fifth engagement element B2 for fixing the carrier Cr of the second planetary gear 6 to the transmission case. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an automatic transmission that shifts the rotation of an input shaft to a plurality of stages through a plurality of planetary gears arranged concentrically with the input shaft and transmits it to an output member.

  Conventionally, as an automatic transmission of this type, according to Patent Document 1, three forward planetary gears and five engaging elements arranged concentrically with an input shaft are used, and six forward stages are used. What performs a shift is known. In this device, the first planetary gear is a double pinion type, and the sun gear is connected to the input shaft.

  Further, a double planetary gear is constructed by connecting a part of the sun gear, carrier and ring gear of the second planetary gear and the third planetary gear to each other. The compound planetary gear includes a first rotating element composed of a sun gear of the third planetary gear, a second rotating element configured by connecting a ring gear of the second planetary gear and a ring gear of the third planetary gear, a carrier of the second planetary gear, and a second planetary gear. A third rotating element configured by connecting a carrier of the three planetary gears, and a fourth rotating element formed of a sun gear of the second planetary gear. These first to fourth rotating elements are arranged in order at intervals corresponding to the gear ratio in the velocity diagram. The first rotating element is connected to the ring gear of the first planetary gear, and the third rotating element is connected to the output member.

  Further, as the engagement element, a first clutch that can be switched between a state in which the fourth rotation element and the input shaft are connected and a state in which the connection is cut off, a state in which the second rotation element and the input shaft are connected, and this connection A second clutch which can be switched to a state where the first rotation element is cut off, a first brake which can be switched between a state where the first rotating element is fixed to the transmission case and a state where the fixing is released, and a second rotating element which is switched to the transmission case A second brake that can be switched between a state of being fixed to the state and a state of releasing the fixing, a third brake that can be switched between a state of fixing the carrier of the first planetary gear to the transmission case and a state of releasing the fixing. It has.

According to the above configuration, the first gear is established by engaging the first clutch and the second brake, the second gear is established by engaging the first clutch and the first brake, The third speed is established by engaging the first clutch and the third brake, the fourth speed is established by engaging the first clutch and the second clutch, and the second clutch and the third brake are engaged. The fifth gear is established by engaging, and the sixth gear is established by engaging the second clutch and the first brake.
Japanese Patent Laying-Open No. 2003-240068 (FIGS. 1 and 2)

  In the above-described conventional example, since three planetary gears arranged in the axial direction are used, the shaft length of the transmission becomes long. Further, in the third speed stage, power is transmitted through all three planetary gears, and the speed stage in which the planetary gear is locked is only the fourth speed stage, and there is a problem that the mesh transmission efficiency is deteriorated.

  In view of the above points, an object of the present invention is to provide an automatic transmission having a short shaft length and high meshing transmission efficiency.

  In order to solve the above-mentioned problems, the present invention provides an automatic transmission that shifts the rotation of an input shaft to a plurality of stages via a plurality of planetary gears arranged concentrically with the input shaft and transmits the speed to an output member. A planetary gear and a second planetary gear are provided, and three elements including a sun gear, a carrier, and a ring gear of the first planetary gear are arranged in the order corresponding to the gear ratio in the speed diagram in the order of arrangement, respectively. The three elements including the sun gear, the carrier, and the ring gear of the second planetary gear are arranged as the fourth element, the fifth element, and the sixth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. One element is connected to the input shaft, the second element is connected to the output shaft, which is an output member arranged parallel to the input shaft, via the first gear train, and the sixth element is connected to the first gear train. A first engagement element that is connected via a second gear train having a different gear ratio and is switchable between a state in which the fourth element and the input shaft are connected and a state in which the connection is cut off; a fifth element and the input shaft; A second engagement element that can be switched between a state in which the connection is disconnected and a state in which the connection is disconnected, and a third engagement element that is switchable between a state in which the third element and the fifth element are connected and a state in which the connection is disconnected A fourth engagement element that can be switched between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released, a state in which the fifth element is fixed to the transmission case, and a state in which the fixation is released And a fifth engagement element that is switchable.

  According to the present invention, as is apparent from the description of the embodiments described later, it is possible to perform a forward six-speed shift. In the present invention, since only the first and second planetary gears arranged in the axial direction are used as the planetary gears, the shaft length of the transmission can be shortened. Further, at the speeds other than the 2nd speed stage and the 3rd speed stage, power is transmitted by only one of the planetary gears of the first and second planetary gears, and at the 2nd speed stage of the 4th speed stage and the 5th speed stage. Since the first planetary gear and the second planetary gear are respectively locked, the mesh transmission efficiency is 100%, and the total transmission efficiency of all the gears is improved.

  In the present invention, when the first element is a sun gear of the first planetary gear, a third planetary gear having a ring gear integrated with the sun gear of the first planetary gear is arranged on the radially inner side of the first planetary gear, If the planetary gear carrier is connected to the fourth element and includes a sixth engagement element that can be switched between a state in which the sun gear of the third planetary gear is fixed to the transmission case and a state in which the fixation is released, the forward eight-stage Can be changed.

  Similarly, in the present invention, when the sixth element is a ring gear of the second planetary gear, a third planetary gear having a sun gear integrated with the ring gear of the second planetary gear is disposed on the radially outer side of the second planetary gear, If the third planetary gear carrier is connected to the fourth element and includes a sixth engagement element that can be switched between a state in which the ring gear of the third planetary gear is fixed to the transmission case and a state in which the fixation is released, the forward movement 8 The gear can be shifted in stages.

  Further, in the present invention, when the fourth element is the sun gear of the second planetary gear, a third planetary gear having a ring gear integrated with the sun gear of the second planetary gear is arranged on the radially inner side of the second planetary gear, If the sun gear of the planetary gear is connected to the input shaft and includes a sixth engagement element that can be switched between a state in which the carrier of the third planetary gear is fixed to the transmission case and a state in which the fixation is released, the forward eight-stage Can be changed.

  In the present invention, the first engagement element may be configured to be switchable between a state in which the carrier of the third planetary gear and the input shaft are connected and a state in which the connection is broken. In this case, if the first engagement element is in a state in which the carrier of the third planetary gear and the input shaft are connected, the rotational speed of the sun gear of the third planetary gear is equal to the rotational speed of the carrier, and the third planetary gear is locked. Thus, the rotational speed of the second planetary gear integrated with the ring gear of the third planetary gear becomes equal to the rotational speed of the input shaft. Accordingly, the first engagement element functions as being switchable between a state in which the sun gear of the second planetary gear as the fourth element and the input shaft are connected and a state in which the connection is cut off.

  And, in any one to which the third planetary gear is added, the third planetary gear is arranged on the inside or outside in the radial direction of one of the first and second planetary gears, so that the transmission function of eight forward speeds is achieved. Despite having it, the shaft length of the transmission does not increase.

  Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. The first embodiment includes an input shaft 2 that is rotatably supported in a transmission case 1 and connected to a power source such as an engine (not shown), and an output shaft that is an output member arranged in parallel with the input shaft 2. 3 is provided. The rotation of the output shaft 3 is transmitted to the left and right drive wheels of the vehicle via a differential gear 4 in which a final driven gear 4a meshing with an output gear 3a fixed to the output shaft 3 is fixed.

  In the transmission case 1, the first planetary gear 5 and the second planetary gear 6 are arranged concentrically with the input shaft 2. The first planetary gear 5 is formed of a single pinion type planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the sun gear Sf and the ring gear Rf so as to freely rotate and revolve.

  With reference to a speed diagram of the first planetary gear 5 shown in the lower part of FIG. 2 (a diagram in which the rotational speeds of the three elements of the sun gear, the carrier, and the ring gear can be represented by straight lines), the sun gear Sf of the first planetary gear 5 Assuming that the three elements comprising the carrier Cf and the ring gear Rf are the first element, the second element, and the third element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, the first element is the sun gear Sf. The second element is the carrier Cf, and the third element is the ring gear Rf. Here, the ratio between the distance between the sun gear Sf and the carrier Cf and the distance between the carrier Cf and the ring gear Rf is i: 1 where the gear ratio of the first planetary gear 5 (number of teeth of the ring gear / number of teeth of the sun gear) is i. Set to In the velocity diagram, the lower horizontal line and the upper horizontal line indicate that the rotational speeds are “0” and “1” (the same rotational speed as the input shaft 2), respectively.

  Similar to the first planetary gear 5, the second planetary gear 6 is of a single pinion type comprising a sun gear Sr, a ring gear Rr, and a carrier Cr that supports the pinion Pr meshing with the sun gear Sr and the ring gear Rr so as to rotate and revolve. It is composed of planetary gears.

  Referring to the speed diagram of the second planetary gear 6 shown in the upper part of FIG. 2, three elements including the sun gear Sr, the carrier Cr, and the ring gear Rr of the second planetary gear 6 are arranged at intervals corresponding to the gear ratio in the speed diagram. If the fourth element, the fifth element, and the sixth element are arranged from the left side in the order in which they are arranged, the fourth element is the sun gear Sr, the fifth element is the carrier Cr, and the sixth element is the ring gear Rr. The ratio between the distance between the sun gear Sr and the carrier Cr and the distance between the carrier Cr and the ring gear Rr is set to j: 1 where j is the gear ratio of the second planetary gear 6.

  The sun gear Sf (first element) of the first planetary gear 5 is connected to the input shaft 2. The carrier Cf (second element) of the first planetary gear 5 has a first gear train G1 including a drive gear G1a fixed to the carrier Cf and a driven gear G1b fixed to the output shaft 3 meshing with the drive gear G1a. The ring gear Rr (sixth element) of the second planetary gear 6 is connected to the output shaft 3 through a drive gear G2a fixed to the ring gear Rr and a driven gear G2b fixed to the output shaft 3 meshing with the drive gear G2a. It is connected to the output shaft 3 via the second gear train G2.

  Here, p> q, where p is the gear ratio of the first gear train G1 (number of teeth of the driven gear / number of teeth of the drive gear) and q is the gear ratio of the second gear train G2. Further, the carrier Cf of the first planetary gear 5 and the ring gear Rr of the second planetary gear 6 are connected by the output shaft 3 via both gear trains G1, G2. The ring gear Rr of the second planetary gear 6 rotates at a speed q / p of the rotation speed of the carrier Cf of the first planetary gear 5.

  In the first embodiment, as the engagement element, a first engagement element that can be switched between a state in which the sun gear Sr (fourth element) of the second planetary gear 6 and the input shaft 2 are connected and a state in which the connection is cut off. A first clutch C1, a second planetary gear 6, a carrier Cr (fifth element) and a second clutch C2 as a second engagement element which can be switched between a state in which the input shaft 2 is connected and a state in which the connection is cut off. A third engaging element that is switchable between a state in which the ring gear Rf (third element) of the first planetary gear 5 and the carrier Cr (fifth element) of the second planetary gear 6 are connected to each other and a state in which the connection is cut off. A first brake B1 as a fourth engagement element that can be switched between a state in which the clutch C3 and the sun gear Sr (fourth element) of the second planetary gear 6 are fixed to the transmission case 1 and a state in which the fixing is released; 2 planets And a capable of switching the fifth engagement element serving the second brake B2 carrier Cr of Rigiya 6 (fifth element) in the state fixed to the transmission case 1 and a state of releasing the fixing.

  In the first embodiment, when the third clutch C3 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1”, and the rotational speed of the ring gear Rf of the first planetary gear 5 is “ 0 ", and the speed line of the first planetary gear 5 becomes a line indicated by" 1st "in FIG. The rotation speed of the carrier Cf of the first planetary gear 5 is 1 / (i + 1), and the output shaft 3 rotates at a speed of 1 / {(i + 1) p} via the first gear train G1. A stage is established.

  When the third clutch C3 and the first brake B1 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at the same speed, and the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. The speed lines of the first planetary gear 5 and the second planetary gear 6 are the lines indicated by “2nd” in FIG. The rotation speed of the carrier Cf of the first planetary gear 5 is (j + 1) p / {(i + 1) (j + 1) p-ijq}, and the rotation speed of the ring gear Rr of the second planetary gear 6 is (j + 1) q / {(i + 1). (J + 1) p−ijq}, and the output shaft 3 rotates at a speed of (j + 1) / {(i + 1) (j + 1) p−ijq} to establish the second gear.

  When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the sun gear Sr of the second planetary gear 6 both become “1”, and the first planetary gear. The ring gear Rf of No. 5 and the carrier Cr of the second planetary gear 6 rotate at the same speed, the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf of the first planetary gear 5, and The speed lines of the first planetary gear 5 and the second planetary gear 6 are the lines indicated by “3rd” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is (i + j + 1) p / {(i + 1) (j + 1) p-ijq}, and the rotational speed of the ring gear Rr of the second planetary gear 6 is (i + j + 1) q / {(i + 1). (J + 1) p-ijq}, and the output shaft 3 rotates at a speed of (i + j + 1) / {(i + 1) (j + 1) p-ijq} to establish the third speed stage.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear. 5 is in a locked state, and the speed line of the first planetary gear 5 is a line indicated by “4th” in FIG. Then, the rotation speed of the carrier Cf of the first planetary gear 5 becomes “1”, the output shaft 3 rotates at a speed of 1 / p, and the fourth speed stage is established.

  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 and the rotational speed of the carrier Cr of the second planetary gear 6 both become “1”, and the second planetary gear. 6 is in a locked state, and the speed line of the second planetary gear 6 is a line indicated by “5th” in FIG. Then, the rotational speed of the ring gear Rr of the second planetary gear 6 becomes “1”, the output shaft 3 rotates at a speed of 1 / q, and the fifth speed stage is established.

  When the second clutch C2 and the first brake B1 are engaged, the rotation speed of the sun gear Sr of the second planetary gear 6 becomes “0”, the rotation speed of the carrier Cr of the second planetary gear 6 becomes “1”, and the second The speed line of the planetary gear 6 is a line indicated by “6th” in FIG. Then, the rotational speed of the ring gear Rr of the second planetary gear 6 becomes (j + 1) / j, the output shaft 3 rotates at a speed of (j + 1) / (jq), and the sixth gear is established.

  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes “1”, the rotational speed of the carrier Cr of the second planetary gear 6 becomes “0”, and the second The speed line of the planetary gear 6 is a line indicated by “Rvs” in FIG. Then, the rotational speed of the ring gear Rr of the second planetary gear 6 becomes -1 / j, the output shaft 3 rotates at a speed of -1 / (jq), and the reverse gear is established.

  A speed line indicated by a dotted line in FIG. 2 represents that each element of the other planetary gear rotates following the one of the first and second planetary gears 5 and 6 that transmits power. .

  FIG. 1B is a diagram summarizing and displaying the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, and C3 and the brakes B1 and B2, and “◯” represents engagement. . FIG. 1B shows that the gear ratio i of the first planetary gear 5 is 2.30, the gear ratio j of the second planetary gear 6 is 3.20, the gear ratio p of the first gear train G1 is 1.32. Also shown is the gear ratio (rotational speed of the input shaft 2 / rotational speed of the output shaft 3) of each gear when the gear ratio q of the two gear train G2 is 0.95. According to this, the public ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (first speed ratio / 6 speed ratio) becomes appropriate.

  Further, according to the first embodiment, since only the first and second planetary gears 5 and 6 are used as the planetary gears, the shaft length of the transmission is larger than that of the conventional example using three planetary gears. Can be shortened. Further, at the speeds other than the 2nd speed stage and the 3rd speed stage, power is transmitted by only one of the first and second planetary gears 5 and 6, and at the 4th speed stage and the 5th speed stage, respectively. Since the first planetary gear 5 and the second planetary gear 6 are in a locked state, the mesh transmission efficiency is 100%, and the total transmission efficiency of all the gears is improved.

  In the first embodiment, each of the first and second planetary gears 5 and 6 is constituted by a single pinion type planetary gear. However, the first planetary gear 5 and the second planetary gear 6 may be constituted by a double pinion type planetary gear. Is possible. When the first planetary gear 5 is formed of a double pinion type planetary gear, one of the sun gear and the carrier is the first element, the ring gear is the second element, and the other of the sun gear and the carrier is the third element. When the second planetary gear 6 is constituted by a double pinion type planetary gear, one of the sun gear and the carrier is the fourth element, the ring gear is the fifth element, and the other of the sun gear and the carrier is the sixth element.

  In the first embodiment, the first gear train G1, the first planetary gear 5, the third clutch C3 and the second brake B2, and the second gear train G2 are sequentially arranged around the input shaft 2 from one end side. Although the second clutch C2, the second planetary gear 6, the first brake B1, and the first clutch C1 are arranged, the present invention is not limited to this. For example, as in the second embodiment shown in FIG. 3, the third clutch C3, the second clutch C2, and the second brake B2 may be arranged between the first gear train G1 and the second gear train G2. . Further, as in the third embodiment shown in FIG. 4, the first brake B1, the second gear train G2, the second planetary gear 6, the first clutch C1, and the second clutch are sequentially arranged from one end side of the input shaft 2. C2, the third clutch C3 and the second brake B2, the first gear train G1, and the first planetary gear 5 may be arranged. It is also possible to dispose the first gear train G1 and the second gear train G2 between the first planetary gear 5 and the second planetary gear 6.

  Next, a fourth embodiment shown in FIG. In the fourth embodiment, a third planetary gear 7 is added to the first embodiment. The third planetary gear 7 is composed of a single pinion type planetary gear including a sun gear Sa, a ring gear Ra, and a carrier Ca that supports a pinion Pa meshing with the sun gear Sa and the ring gear Ra so as to rotate and revolve. Then, the sun gear Sf of the first planetary gear 5 and the ring gear Ra of the third planetary gear 7 are integrated, and the third planetary gear 7 is disposed radially inward of the first planetary gear 5.

  The carrier Ca of the third planetary gear 7 is connected to the sun gear Sr of the second planetary gear 6 that is the fourth element. Furthermore, a third brake B3, which is a sixth engagement element that can be switched between a state in which the sun gear Sa of the third planetary gear 7 is fixed to the transmission case 1 and a state in which the fixation is released, is added as an engagement element. . Other configurations are the same as those of the first embodiment.

  With reference to the speed diagram of the third planetary gear 7 shown in the upper part of FIG. 6, the rotational speed of the ring gear Ra of the third planetary gear 7 is always “1”. When the third brake B3 is engaged, the rotational speed of the sun gear Sa of the third planetary gear 7 becomes “0”. Therefore, the carrier Ca of the third planetary gear 7 and the sun gear Sr of the second planetary gear 6 coupled thereto. The rotation speed is k / (k + 1), where k is the gear ratio of the third planetary gear 7.

  In the fourth embodiment, when the third clutch C3 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1”, and the rotational speed of the ring gear Rf of the first planetary gear 5 is “0”. The speed line of the first planetary gear 5 becomes a line indicated by “1st” in FIG. The rotation speed of the carrier Cf of the first planetary gear 5 is 1 / (i + 1), and the output shaft 3 rotates at a speed of 1 / {(i + 1) p} via the first gear train G1. A stage is established.

  When the third clutch C3 and the first brake B1 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at the same speed, and the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. The speed lines of the first planetary gear 5 and the second planetary gear 6 are shown by “2nd” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is (j + 1) q / {(i + 1) (j + 1) q-ijp}, and the rotational speed of the ring gear Rr of the second planetary gear 6 is (j + 1) p / {(i + 1). (J + 1) q-ijp}, and the output shaft 3 rotates at a speed of (j + 1) / {(i + 1) (j + 1) q-ijp} to establish the second gear.

  When the third clutch C3 and the third brake B3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1”, and the rotational speed of the sun gear Sr of the second planetary gear 6 is k / (k + 1). The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at the same speed, and the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. Thus, the speed lines of the first planetary gear 5 and the second planetary gear 6 are the lines indicated by “3rd” in FIG. The rotation speed of the carrier Cf of the first planetary gear 5 is {j + 1 + ik / (k + 1)} p / {(i + 1) (j + 1) p-ijq}, and the rotation speed of the ring gear Rr of the second planetary gear 6 is {j + 1 + ik / (K + 1)} q / {(i + 1) (j + 1) p-ijq}, and the output shaft 3 rotates at a speed of {j + 1 + ik / (k + 1)} / {(i + 1) (j + 1) p-ijq} Third gear is established.

  When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the sun gear Sr of the second planetary gear 6 both become “1”, and the first planetary gear. The ring gear Rf of No. 5 and the carrier Cr of the second planetary gear 6 rotate at the same speed, the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf of the first planetary gear 5, and The speed lines of the first planetary gear 5 and the second planetary gear 6 are indicated by “4th” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is (i + j + 1) p / {(i + 1) (j + 1) p-ijq}, and the rotational speed of the ring gear Rr of the second planetary gear 6 is (i + j + 1) q / {(i + 1). (J + 1) p−ijq}, and the output shaft 3 rotates at a speed of (i + j + 1) / {(i + 1) (j + 1) p−ijq} to establish the fourth speed stage.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear 5 Is in a locked state, and the speed line of the first planetary gear 5 becomes a line indicated by "5th" in FIG. Then, the rotation speed of the carrier Cf of the first planetary gear 5 becomes “1”, the output shaft 3 rotates at a speed of 1 / p, and the fifth speed stage is established.

  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 and the rotational speed of the carrier Cr of the second planetary gear 6 both become “1”, and the second planetary gear. 6 is in a locked state, and the speed line of the second planetary gear 6 is a line indicated by “6th” in FIG. Then, the rotational speed of the ring gear Rr of the second planetary gear 6 becomes “1”, the output shaft 3 rotates at a speed of 1 / q, and the sixth speed stage is established.

  When the second clutch C2 and the third brake B3 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 is k / (k + 1), and the rotational speed of the carrier Cr of the second planetary gear 6 is “1”. The speed line of the second planetary gear 6 is a line indicated by “7th” in FIG. The rotational speed of the ring gear Rr of the second planetary gear 6 is {(j + 1) −k / (k + 1)} / j, and the output shaft 3 is a speed of {(j + 1) −k / (k + 1)} / (jq). To establish the seventh gear.

  When the second clutch C2 and the first brake B1 are engaged, the rotation speed of the sun gear Sr of the second planetary gear 6 becomes “0”, the rotation speed of the carrier Cr of the second planetary gear 6 becomes “1”, and the second The speed line of the planetary gear 6 is a line indicated by “8th” in FIG. Then, the rotational speed of the ring gear Rr of the second planetary gear 6 becomes (j + 1) / j, the output shaft 3 rotates at a speed of (j + 1) / (jq), and the eighth gear is established.

  When the second brake B2 and the third brake B3 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes k / (k + 1), and the rotational speed of the carrier Cr of the second planetary gear 6 becomes “0”. The speed line of the second planetary gear 6 is a line indicated by “Rvs1” in FIG. Then, the rotation speed of the ring gear Rr of the second planetary gear 6 becomes −k / {(k + 1) j}, the output shaft 3 rotates at a speed of −k / {(k + 1) jq}, and the reverse first speed is set. Established.

  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes “1”, the rotational speed of the carrier Cr of the second planetary gear 6 becomes “0”, and the second The speed line of the planetary gear 6 is a line indicated by “Rvs2” in FIG. Then, the rotational speed of the ring gear Rr of the second planetary gear 6 becomes -1 / j, the output shaft 3 rotates at a speed of -1 / (jq), and the second reverse speed stage is established.

  FIG. 5B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, and C3 and the brakes B1, B2, and B3. “O” represents engagement. ing. FIG. 5B shows that the gear ratio i of the first planetary gear 5 is 2.40, the gear ratio j of the second planetary gear 6 is 2.10, the gear ratio k of the third planetary gear 7 is 2.20, The gear ratios of the respective gears are also shown when the gear ratio p of the gear train G1 is 1.18 and the gear ratio q of the second gear train G2 is 0.95.

  According to the fourth embodiment, since the third planetary gear 7 is disposed radially inward of the first planetary gear 5, the shaft length of the transmission does not increase despite having a gear shifting function of eight forward speeds.

  Next, a fifth embodiment shown in FIG. 5th Embodiment adds the 3rd planetary gear 7 to 1st Embodiment similarly to 4th Embodiment. The third planetary gear 7 is composed of a single pinion type planetary gear including a sun gear Sa, a ring gear Ra, and a carrier Ca that supports a pinion Pa meshing with the sun gear Sa and the ring gear Ra so as to rotate and revolve. In the fifth embodiment, the sun gear Sa of the third planetary gear 7 and the ring gear Rr of the second planetary gear 6 are integrated, and the third planetary gear 7 is disposed on the radially outer side of the second planetary gear 6.

  The carrier Ca of the third planetary gear 7 is connected to the sun gear Sr of the second planetary gear 6 that is the fourth element. Further, a third brake B3, which is a sixth engagement element that can be switched between a state in which the ring gear Ra of the third planetary gear 7 is fixed to the transmission case 1 and a state in which the fixation is released, is added as an engagement element. . Other configurations are the same as those of the first embodiment.

  In the fifth embodiment, the second planetary gear 6 and the third planetary gear 7 constitute a double planetary gear. 8, the ring gear Ra of the third planetary gear 7 is positioned on the vertical line Y1, and the carrier Ca of the third planetary gear 7 and the sun gear Sr of the second planetary gear 6 are on the vertical line Y2. , The carrier Cr of the second planetary gear 6 is positioned on the vertical line Y3, and the sun gear Sa of the third planetary gear 7 and the ring gear Rr of the second planetary gear 6 are positioned on the vertical line Y4. Here, if the interval between the vertical line Y4 and the vertical line Y3 is 1, the interval between the vertical line Y3 and the vertical line Y2 is j (j is the gear ratio of the second planetary gear 6). The interval between Y2 and the vertical line Y1 is (j + 1) / k (k is the gear ratio of the third planetary gear 7).

  In this case, when the third clutch C3 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is "1", and the rotational speed of the ring gear Rf of the first planetary gear 5 is "0". Become. Then, the speed line of the first planetary gear 5 becomes a line indicated by “1st” in FIG. 8, and the first gear is established.

  When the third clutch C3 and the first brake B1 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at a constant speed, and the ring gear Rr of the second planetary gear 6 rotates at a speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. Then, the speed lines of the first planetary gear 5 and the double planetary gear become a line indicated by “2nd” in FIG. 8, and the second speed stage is established.

  When the third clutch C3 and the third brake B3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the ring gear Ra of the third planetary gear 7 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at a constant speed, and the ring gear Rr of the second planetary gear 6 rotates at a speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. Then, the speed lines of the first planetary gear 5 and the double planetary gear become a line indicated by “3rd” in FIG. 8, and the third speed stage is established.

  When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the sun gear Sr of the second planetary gear 6 become “1”, and the first planetary gear 5 The ring gear Rf of the second planetary gear 6 and the carrier Cr of the second planetary gear 6 rotate at the same speed, and the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. Then, the speed lines of the first planetary gear 5 and the double planetary gear are shown by “4th” in FIG. 8, and the fourth speed stage is established.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear 5 Is locked. Then, the speed line of the first planetary gear 5 becomes a line indicated by “5th” in FIG. 8, and the fifth speed stage is established.

  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 and the rotational speed of the carrier Cr of the second planetary gear 6 both become “1”, and the second planetary gear. 6 is locked. Then, the speed line of the double planetary gear becomes a line indicated by “6th” in FIG. 8, and the 6th speed stage is established.

  When the second clutch C2 and the third brake B3 are engaged, the rotational speed of the ring gear Ra of the third planetary gear 6 is “0”, and the rotational speed of the carrier Cr of the second planetary gear 6 is “1”. Then, the speed line of the double planetary gear becomes a line indicated by “7th” in FIG. 8, and the seventh speed stage is established.

  When the second clutch C2 and the first brake B1 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 is “0”, and the rotational speed of the carrier Cr of the second planetary gear 6 is “1”. And the speed line of the 2nd planetary gear 6 turns into a line shown as "8th" in Drawing 8, and the 8th gear stage is established.

  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 is “1”, and the rotational speed of the carrier Cr of the second planetary gear 6 is “0”. Then, the speed line of the compound planetary gear becomes a line indicated by “Rvs” in FIG. 8, and the reverse gear is established.

  FIG. 7B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, and C3 and the brakes B1, B2, and B3. “O” represents engagement. ing. Also in the fifth embodiment, it is possible to perform eight forward shifts. And since the 3rd planetary gear 7 is arrange | positioned in the radial direction outer side of the 2nd planetary gear 6, the axial length of a transmission does not increase.

  Next, a sixth embodiment shown in FIG. In the sixth embodiment, a third planetary gear 7 is added. The third planetary gear 7 is composed of a single pinion type planetary gear including a sun gear Sa, a ring gear Ra, and a carrier Ca that supports a pinion Pa meshing with the sun gear Sa and the ring gear Ra so as to rotate and revolve. In the sixth embodiment, the third planetary gear 7 is arranged radially inward of the second planetary gear 6 by integrating the ring gear Ra of the third planetary gear 7 with the sun gear Sr of the second planetary gear 6 as the fourth element. .

  The sun gear Sa of the third planetary gear 7 is connected to the input shaft 2. In each of the above embodiments, the sun gear Sr of the second planetary gear 6 is connected to the input shaft 2 via the first clutch C1, but in the sixth embodiment, the carrier Ca of the third planetary gear 7 is connected to the first clutch. It is connected to the input shaft 2 via C1. Further, as an engagement element, a third brake B3 is added as a sixth engagement element that can be switched between a state in which the carrier Ca of the third planetary gear 7 is fixed to the transmission case 1 and a state in which the fixation is released. . Other configurations are the same as those of the first embodiment.

  Referring to the speed diagram of the third planetary gear 7 shown in the upper part of FIG. 10, when the first clutch C1 is engaged, the rotational speed of the sun gear Sa of the third planetary gear 7 and the rotational speed of the carrier Ca are both “1”. The third planetary gear 7 is locked, and the rotational speed of the sun gear Sr of the second planetary gear 6 integrated with the ring gear Ra of the third planetary gear 7 becomes “1”. Accordingly, also in the sixth embodiment, the first clutch C1 has a first engagement that can be switched between a state in which the sun gear Sr of the second planetary gear 6 as the fourth element and the input shaft 2 are connected and a state in which the connection is cut off. Acts as an element. As in the first embodiment, the sun gear Sr of the second planetary gear 6 may be connected to the input shaft 2 via the first clutch C1.

  When the third brake B3 is engaged, the rotation speed of the carrier Ca of the third planetary gear 7 becomes “0”, and the rotation speed of the sun gear Sr of the second planetary gear 6 is −1 / k (k is the third planetary gear). 3 gear ratio).

  In the sixth embodiment, when the third clutch C3 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1”, and the rotational speed of the ring gear Rf of the first planetary gear 5 is “0”. "become. Then, the speed line of the first planetary gear 5 becomes a line indicated by “1st” in FIG. 10, and the first gear is established.

  When the third clutch C3 and the third brake B3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1”, the rotational speed of the sun gear Sr of the second planetary gear 6 is −1 / k, The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at a constant speed, and the ring gear Rr of the second planetary gear 6 rotates at a speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. . And the speed line of the 1st planetary gear 5 and the 2nd planetary gear 6 turns into a line shown as "2nd" in Drawing 10, and the 2nd gear stage is established.

  When the third clutch C3 and the first brake B1 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the sun gear Sr of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cr of the second planetary gear 6 rotate at a constant speed, and the ring gear Rr of the second planetary gear 6 rotates at a speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. And the speed line of the 1st planetary gear 5 and the 2nd planetary gear 6 turns into a line shown as "3rd" in Drawing 10, and the 3rd gear stage is established.

  When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the sun gear Sr of the second planetary gear 6 become “1”, and the first planetary gear 5 The ring gear Rf of the second planetary gear 6 and the carrier Cr of the second planetary gear 6 rotate at the same speed, and the ring gear Rr of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. And the speed line of the 1st planetary gear 5 and the 2nd planetary gear 6 turns into a line shown as "4th" in Drawing 10, and the 4th gear stage is established.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear 5 Is locked. Then, the speed line of the first planetary gear 5 becomes a line indicated by “5th” in FIG. 10, and the fifth speed stage is established.

  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 and the rotational speed of the carrier Cr of the second planetary gear 6 both become “1”, and the second planetary gear. 6 is locked. Then, the speed line of the double planetary gear becomes a line indicated by “6th” in FIG. 10, and the 6th speed stage is established.

  When the second clutch C2 and the first brake B1 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 is “0”, and the rotational speed of the carrier Cr of the second planetary gear 6 is “1”. Then, the speed line of the second planetary gear 6 becomes a line indicated by “7th” in FIG. 10, and the seventh speed stage is established.

  When the second clutch C2 and the third brake B3 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 is -1 / k, and the rotational speed of the carrier Cr of the second planetary gear 6 is "1". Then, the speed line of the double planetary gear becomes a line indicated by “8th” in FIG. 10, and the eighth speed stage is established.

  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the sun gear Sr of the second planetary gear 6 is “1”, and the rotational speed of the carrier Cr of the second planetary gear 6 is “0”. Then, the speed line of the double planetary gear becomes a line indicated by “Rvs” in FIG. 10, and the reverse gear is established.

  FIG. 9B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, and C3 and the brakes B1, B2, and B3. “◯” represents engagement. ing. Also in the sixth embodiment, eight forward speeds can be changed. And since the 3rd planetary gear 7 is arrange | positioned at the radial inside of the 2nd planetary gear 6, the axial length of a transmission does not increase.

  In addition, also in the thing of 4th-6th embodiment, the arrangement position of each engagement element can be changed. For example, in the fourth embodiment, the third clutch C3 and the second brake B2 are arranged between the first planetary gear 5 and the third planetary gear 7 and the second gear train G2, but the seventh embodiment shown in FIG. As described above, the third clutch C3 is disposed adjacent to the second clutch C2 between the second gear train G2 and the second planetary gear 6, and the first brake B1 is adjacent to the first brake B1 on one axial side of the second planetary gear 6. Two brakes B2 may be arranged.

  In the sixth embodiment, the third clutch C3 and the second brake B2 are disposed between the first planetary gear 5 and the second gear train G2. However, as in the eighth embodiment shown in FIG. A third clutch C3 is disposed adjacent to the second clutch C2 between the row G2 and the second planetary gear 6 and the third planetary gear 7, and the first brake B1 is disposed on one axial side of the second planetary gear 6 and the third planetary gear 7. The second brake B2 may be disposed adjacent to the second brake B2.

  Moreover, although the said embodiment is an automatic transmission for FF vehicles, if a propeller shaft is connected with the output shaft 3, it can also be set as the automatic transmission for FR vehicles.

(A) Skeleton diagram of the first embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st planetary gear and 2nd planetary gear of 1st Embodiment. The skeleton figure of 2nd Embodiment of this invention transmission. The skeleton figure of 3rd Embodiment of this invention transmission. (A) Skeleton diagram of the fourth embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st-3rd planetary gear of 4th Embodiment. (A) Skeleton diagram of a fifth embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st planetary gear of 5th Embodiment and a double type planetary gear. (A) Skeleton diagram of the sixth embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st-3rd planetary gear of 6th Embodiment. The skeleton figure of 7th Embodiment of this invention. The skeleton figure of 8th Embodiment of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output shaft, 5 ... 1st planetary gear, Sf ... Sun gear (1st element) of 1st planetary gear, Cf ... Carrier (2nd element) of 1st planetary gear, Rf ... Ring gear (third element) of first planetary gear, 6 ... second planetary gear, Sr ... Sun gear (fourth element) of second planetary gear, Cr ... Carrier (fifth element) of second planetary gear, Rr ... Ring gear of second planetary gear (Sixth element), 7 ... third planetary gear, Sa ... sun gear of the third planetary gear, Ca ... carrier of the third planetary gear, Ra ... ring gear of the third planetary gear, G1 ... first gear train, G2 ... second gear train, C1 ... 1st clutch (1st engagement element), C2 ... 2nd clutch (2nd engagement element), C3 ... 3rd clutch (3rd engagement element), B1 ... First brake (4th engagement element), B2 ... second brake (Fifth engagement element), B3 ... third brake (Sixth engagement element).

Claims (5)

An automatic transmission that shifts the rotation of the input shaft to a plurality of stages via a plurality of planetary gears arranged concentrically with the input shaft, and transmits it to the output member,
A first planetary gear and a second planetary gear;
The three elements including the sun gear, the carrier, and the ring gear of the first planetary gear are set as the first element, the second element, and the third element in the order corresponding to the gear ratio in the velocity diagram, respectively, and the sun gear of the second planetary gear , The three elements consisting of the carrier and the ring gear are respectively arranged as a fourth element, a fifth element and a sixth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram.
The first element is connected to the input shaft, the second element is connected to the output shaft, which is an output member arranged parallel to the input shaft, via the first gear train, and the sixth element is the first gear train. Are connected via a second gear train of different gear ratios,
A first engagement element switchable between a state in which the fourth element and the input shaft are connected and a state in which the connection is cut off;
A second engagement element that is switchable between a state in which the fifth element and the input shaft are connected and a state in which the connection is cut off;
A third engagement element switchable between a state in which the third element and the fifth element are connected and a state in which the connection is broken;
A fourth engagement element switchable between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising a fifth engagement element that is switchable between a state in which the fifth element is fixed to the transmission case and a state in which the fixation is released.   The first element is a sun gear of the first planetary gear, a third planetary gear having a ring gear integrated with the sun gear of the first planetary gear is disposed radially inward of the first planetary gear, and the carrier of the third planetary gear is the 2. The automatic engagement device according to claim 1, further comprising a sixth engagement element connected to the fourth element and capable of switching between a state in which the sun gear of the third planetary gear is fixed to the transmission case and a state in which the fixation is released. transmission.   The sixth element is a ring gear of the second planetary gear, and a third planetary gear having a sun gear integrated with the ring gear of the second planetary gear is disposed on the radially outer side of the second planetary gear, and the carrier of the third planetary gear is the first planetary gear. The automatic transmission according to claim 1, further comprising a sixth engagement element connected to the four elements and capable of switching between a state in which the ring gear of the third planetary gear is fixed to the transmission case and a state in which the fixation is released. Machine.   The fourth element is a sun gear of the second planetary gear, and a third planetary gear having a ring gear integrated with the sun gear of the second planetary gear is disposed radially inward of the second planetary gear, and the sun gear of the third planetary gear is The automatic transmission according to claim 1, further comprising a sixth engagement element connected to the input shaft and capable of switching between a state in which the carrier of the third planetary gear is fixed to the transmission case and a state in which the carrier is released. Machine.   5. The automatic transmission according to claim 4, wherein the first engagement element is configured to be switchable between a state in which the carrier of the third planetary gear and the input shaft are connected and a state in which the connection is broken.

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