JP2009174643A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce friction losses by disengaged engagement elements by engaging three engagement elements in each speed change stage in an automatic transmission comprising a planetary gear for deceleration, a double planetary gear for speed change, and six engagement elements. <P>SOLUTION: Four elements of the double planetary gear 5 for speed change are defined as second, third and fourth elements in the order in a velocity diagram, three elements of the planetary gear 4 for deceleration are defined as fifth, sixth and seventh elements in the order in the velocity diagram, and the first element Sm1 is connected to the sixth element Cf. There are provided first, second and third engagement elements C1, C2, C3 for respectively connecting an input member 2 to the fifth element Sf, the second element Cm, and the fourth element Sms, a fourth engagement element C4 for connecting the second element Cm to the seventh element Rf, a fifth engagement element B1 for fixing the fifth element Sf, and a sixth engagement element B2 for fixing the seventh element Rf. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an automatic transmission provided with a shift type planetary gear for shifting the rotation of an input member to a plurality of stages and transmitting it to an output member.

  Conventionally, Patent Document 1 discloses an automatic transmission that can perform a forward eight-speed shift using a speed reduction planetary gear, a speed change double planetary gear, and six engagement elements. The double planetary gear for shifting has four rotating elements configured by connecting parts of the sun gear, the carrier, and the ring gear of the two planetary gears to each other. For example, a first rotating element configured by connecting a sun gear of one planetary gear and a carrier of the other planetary gear, and a second configured by connecting a carrier of one planetary gear and a ring gear of the other planetary gear. A rotating element; a third rotating element formed of a ring gear of one planetary gear; and a fourth rotating element formed of a sun gear of the other planetary gear. These first to fourth rotating elements are arranged in order at intervals corresponding to the gear ratio in the velocity diagram. The third rotating element is coupled to the output member.

  Further, as the engaging element, a first clutch that can be switched between a state in which the rotation of the input member is transmitted to the fourth rotating element via the speed reduction planetary gear and a state in which the transmission is cut off, and a speed reduction planetary gear for the rotation of the input member A second clutch that can be switched between a state of transmitting to the first rotating element via the first and a state of disconnecting the transmission, a state of connecting the input member and the second rotating element, and a state of disconnecting the connection. A third clutch, a fourth clutch that can be switched between a state in which the input member and the first rotating element are connected to each other, and a state in which the connection is disconnected; a state in which the first rotating element is fixed to the transmission case; A first brake that can be switched to a state of being engaged, and a second brake that is switchable to a state of fixing the second rotating element to the transmission case and a state of releasing the fixing.

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 gear is established by engaging the first and second clutches, the fourth gear is established by engaging the first and fourth clutches, and the first and third clutches are engaged. The fifth gear is established by engaging, the sixth gear is established by engaging the third and fourth clutches, and the seventh gear is established by engaging the second and third clutches. Is established, and the eighth gear is established by engaging the third clutch and the first brake.
JP2003-130152A (FIGS. 1 and 2)

  In the above conventional example, the number of engaging elements to be engaged at each shift stage is two. For this reason, there is a problem that the friction loss due to dragging of the remaining four engagement elements that have been released increases and the efficiency of the transmission deteriorates.

  In view of the above points, the present invention allows three engagement elements to be engaged at each shift stage among the six engagement elements to reduce the friction loss due to the released engagement elements. The problem is to provide an automatic transmission.

  In order to solve the above-mentioned problem, the first invention of the present application shifts the rotation of the input member to a plurality of stages via a speed reduction planetary gear and a speed change planetary gear arranged in the transmission case, and transmits them to the output member. In the automatic transmission, the dual planetary gear for shifting has four rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the order of arrangement in the speed diagram, respectively. The third element, the third element, and the fourth element, and the three elements including the sun gear, the ring gear, and the carrier of the speed reduction planetary gear, are arranged in the order corresponding to the gear ratio in the speed diagram, respectively, in the order of arrangement. As the seventh element, the first element and the sixth element are connected, the third element is connected to the output member, the input member and the fifth element are connected, and the connection is broken. The first engaging element, which can be switched between, the input member and the second element are connected, and the second engaging element which is switchable between the state where the connection is disconnected and the state where the connection is broken, and the input member and the fourth element are connected. A third engagement element that is switchable between a state and a state in which this connection is cut off, a fourth engagement element that is switchable between a state in which the second element and the seventh element are connected, and a state in which this connection is cut off, A fifth engagement element that can be switched between a state in which the five elements are fixed to the transmission case and a state in which the fixing is released, and a state in which the seventh element is fixed to the transmission case and a state in which the fixing is released are switched. And a free sixth engaging element.

  Further, the second invention of the present application is obtained by replacing the speed reduction planetary gear of the first invention with a speed reduction double planetary gear. The second element, the third element, and the fourth element, and the four rotating elements of the deceleration type planetary gear are arranged in the speed diagram in the order of arrangement as the fifth element, the sixth element, the seventh element, and the eighth element, respectively. And the sixth element are connected, the third element is connected to the output member, and the first engagement element is switchable between a state of connecting the input member and the fifth element and a state of disconnecting the connection, Switchable between a state where the input member and the second element are connected and a state where the connection is cut off, a state where the input member and the fourth element are connected and a state where the connection is cut off. A third engagement element and a second Switchable between a state where the element and the eighth element are connected and a state where the connection is cut off, a fourth engaging element, a state where the seventh element is fixed to the transmission case, and a state where the fixing is released A fifth engagement element, and a sixth engagement element switchable between a state in which the eighth element is fixed to the transmission case and a state in which the fixation is released.

  According to the first invention, as will be apparent from the description of the embodiment described later, it is possible to perform eight forward shifts, and among the first to sixth six engagement elements, three shift gears are provided. The engagement elements are engaged. Further, according to the second invention, as will be apparent from the description of the embodiment described later, it is possible to perform the forward 10-speed shift, and among each of the first to sixth engaging elements, the respective shift speeds. In this case, three engaging elements are engaged. In both the first invention and the second invention, the number of engagement elements released at each shift stage is three. Therefore, as compared with the conventional example in which four engagement elements are released, the friction loss due to the released engagement elements can be reduced, and the efficiency of the transmission is improved.

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

  Further, in the transmission case 1, a speed reduction planetary gear 4 and a speed change double planetary gear 5 are arranged around the input shaft 2. The shift type planetary gear 5 includes a first sun gear Sml, a second sun gear Sms, a ring gear Rm, a first pinion Pml, a second sun gear Sms, and a first pinion Pml that mesh with the first sun gear Sml and the ring gear Rm. It is composed of a Ravigneaux type planetary gear having a carrier Cm that supports the meshing second pinion Pms so as to rotate and revolve.

  Referring to the speed diagram of the speed-changing planetary gear 5 shown in the lower part of FIG. 2 (the speed of the plurality of rotating elements constituting the planetary gear can be represented by straight lines), the first sun gear of the speed-changing planetary gear 5 is shown. Four rotating elements consisting of Sml, second sun gear Sms, ring gear Rm and carrier Cm are arranged in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram from the left side, the first element, second element, third element and Assuming the fourth element, the first element is the first sun gear Sml, the second element is the carrier Cm, the third element is the ring gear Rm, and the fourth element is the second sun gear Sms. Here, the gear ratio between the ring gear Rm and the first sun gear Sml (the number of teeth of the ring gear Rm / the number of teeth of the first sun gear Sml) is j1, and the gear ratio between the ring gear Rm and the second sun gear Sms (the number of teeth of the ring gear Rm / J2 as the number of teeth of the second sun gear Sms), the interval between the vertical line Y2 where the first sun gear Sml is located and the vertical line Y3 where the carrier Cm is located, and between the vertical line Y3 and the vertical line Y4 where the ring gear Rm is located. The ratio of the interval and the interval between the vertical line Y4 and the vertical line Y5 where the second sun gear Sms is located is set to j1: 1: j2-1. Further, the lower horizontal line and the upper horizontal line of the velocity diagram indicate that the rotational speeds are “0” and “1” (the same rotational speed as that of the input shaft 2), respectively.

  The reduction planetary gear 4 is constituted by a single planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the pinion Pf meshing with the sun gear Sf and the ring gear Rf so as to be capable of rotating and revolving. Referring to the speed diagram of the speed reduction planetary gear 4 shown in the upper part of FIG. 2, the three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the speed reduction planetary gear 4 are arranged at intervals corresponding to the gear ratio in the speed diagram. The fifth element is the sun gear Sf, the sixth element is the carrier Cf, and the seventh element is the ring gear Rf. 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: where the gear ratio of the speed reduction planetary gear 4 (number of teeth of the ring gear Rf / number of teeth of the sun gear Sf) is i: 1 is set. The output speed of the planetary gear 4 for deceleration when the rotational speed of the sun gear Sf becomes “1” and the rotational speed of the ring gear Rf becomes “0” due to the engagement of the first clutch C1 and the second brake B2, which will be described later. The rotation speed N1 of the carrier Cf is 1 / (i + 1).

  Here, in the present embodiment, the first sun gear Sml (first element) of the speed-changing planetary gear 5 and the carrier Cf (sixth element) of the speed-down planetary gear 4 are connected, and the ring gear Rm of the speed-changing planetary gear 5 is also connected. The (third element) is connected to the output gear 3. Further, as an engagement element, a first clutch C1 as a first engagement element that can be switched between a state in which the input shaft 2 and the sun gear Sf (fifth element) of the speed reduction planetary gear 4 are connected and a state in which the connection is cut off. A second clutch C2 as a second engagement element that can be switched between a state in which the input shaft 2 and the carrier Cm (second element) of the transmission-use planetary gear 5 are connected and a state in which the connection is cut off; The third clutch C3, which is a third engagement element that can be switched between a state in which the second sun gear Sms (fourth element) of the transmission-use planetary gear 5 is connected and a state in which the connection is cut off, and a carrier of the transmission-use planetary gear 5 A fourth clutch C4 as a fourth engagement element that can be switched between a state in which Cm (second element) and the ring gear Rf (seventh element) of the speed reduction planetary gear 4 are connected and a state in which the connection is disconnected; A first brake B1, which is a fifth engagement element that can be switched between a state in which the sun gear Sf (fifth element) of the spur gear 4 is fixed to the transmission case 1 and a state in which the fixing is released, and a ring gear of the planetary gear 4 for the speed reducer. A second brake B2 is provided as a sixth engaging element that can be switched between a state in which Rf (seventh element) is fixed to the transmission case 1 and a state in which the fixing is released.

  By connecting the carrier Cf of the speed reduction planetary gear 4 and the first sun gear Sml of the speed change double planetary gear 5 as described above, the carrier Cf of the speed reduction planetary gear 4 in the speed diagram of the double planetary gear 5 shown in the lower part of FIG. Is located on the same vertical line Y2 as the first sun gear Sml of the double planetary gear 5 for shifting. When the fourth clutch C4 is engaged, the ring gear Rf of the speed reduction planetary gear 4 is positioned on the same vertical line Y3 as the carrier Cm of the speed change double planetary gear 5, and the sun gear Sf of the speed reduction planetary gear 4 is It is located on the vertical line Y1 that is separated from the vertical line Y2 to the left by i times the interval between Y2 and the vertical line Y3.

  In this embodiment, when the third clutch C3, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y3 is “0”, and the rotational speed at the vertical line Y5 is “1”. Thus, the rotational speed at the vertical line Y4 where the ring gear Rm of the shift type planetary gear 5 connected to the output gear 3 is located is “1st”. That is, the first gear is established.

  When the third clutch C3, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y5 is "1", and the vertical line Y4 The rotation speed at is 2nd. That is, the second gear is established.

  When the third clutch C3, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y1 is "0", the rotational speed at the vertical line Y5 is "1", and the vertical line Y4 The rotation speed at is “3rd”. That is, the third gear is established.

  When the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y5 is “1”, and the rotational speed at the vertical line Y4 is The rotation speed is “4th”. That is, the fourth gear is established.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed at the vertical line Y3 and the rotational speed at the vertical line Y5 are both “1”, and the rotational speed at the vertical line Y4 is also “1”. "5th". That is, the fifth gear is established. Even if one of the first brake B1 and the second brake B2 is engaged, the fifth gear is established by engaging the second clutch C2 and the third clutch C3.

  When the second clutch C2, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y1 is "0", the rotational speed at the vertical line Y3 is "1", and the vertical line Y4 The rotation speed at is “6th”. That is, the sixth gear is established.

  When the first clutch C1, the second clutch C2, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is "1", and the vertical line Y4 The rotation speed is “7th”. That is, the seventh gear is established.

  When the second clutch C2, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y3 is "1", and the vertical line Y4 The rotation speed at is “8th”. That is, the eighth gear is established.

  When the first clutch C1, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “0”, and the rotational speed at the vertical line Y4 is The rotation speed becomes negative “Rev”. That is, the reverse gear is established.

  FIG. 1B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2, and ◯ represents engagement. Note that (◯) of the first brake B1 and the second brake B2 at the fifth speed represents that either one of the first brake B1 and the second brake B2 is engaged. Here, in the fourth speed, the third clutch C3 and the second brake B2 that are engaged even in the first clutch C1 and the fifth speed are engaged, so the first clutch C1 is released and the second clutch C2 is engaged. By combining, the upshift is performed from the fourth gear to the fifth gear. At the sixth speed, the second clutch C2, the fourth clutch C4, and the first brake B1 that are engaged even at the fifth speed are engaged, so that the second brake B2 is replaced after the upshift to the fifth speed. If the first brake B1 is engaged, the third clutch C3 is released and the fourth clutch is engaged, so that the fifth speed is increased to the sixth speed.

  FIG. 1B shows the gear ratio (input shaft 2) of each gear position when the gear ratios i, j1, and j2 are i = 1.3, j1 = 1.4, and j2 = 3.5, respectively. (Rotational speed of the output gear 3 / rotational speed of the output gear 3). According to this, the common ratio (ratio of gear ratios between gears) becomes appropriate, and the range (first speed ratio / 8 speed ratio) becomes appropriate.

  In the present embodiment, among the six engagement elements, three engagement elements are engaged at each shift speed, so the number of engagement elements released at each shift speed is three. Therefore, compared to the conventional example in which the four engagement elements are released, the friction loss due to the released engagement elements can be reduced, and the efficiency of the transmission is improved.

  By the way, in the said 1st Embodiment, although the double planetary gear 5 for transmission was comprised by the Ravigneaux type planetary gear, it is not restricted to this. For example, as in the second embodiment shown in FIG. 3, a first planetary gear having a sun gear Sm1, a ring gear Rm1, and a carrier Cm1 that supports a pinion Pm1 meshing with the sun gear Sm1 and the ring gear Rm1 so as to rotate and revolve. A first planetary gear 51, a sun gear Sm2, a ring gear Rm2, and a second planetary gear 52 composed of a single planetary gear having a carrier Cm2 that supports the sun gear Sm2 and the pinion Pm2 meshing with the ring gear Rm2 so as to rotate and revolve. The carrier Cm1 of the first planetary gear 51 and the ring gear Rm2 of the second planetary gear 52 are connected, and the ring gear Rm1 of the first planetary gear 51 and the carrier Cm2 of the second planetary gear 52 are connected to form the transmission-use planetary gear 5. It may be.

  The double planetary gear 5 for shifting according to the second embodiment includes a sun gear Sm1 of the first planetary gear 51, a sun gear Sm2 of the second planetary gear 52, a carrier Cm1 of the first planetary gear 51, and a ring gear Rm2 of the second planetary gear 52 ( The first rotating body includes four rotating elements including a first connecting body and a connecting body (second connecting body) of the ring gear Rm1 of the first planetary gear 51 and the carrier Cm2 of the second planetary gear 52. Then, assuming that these rotating elements are a first element, a second element, a third element, and a fourth element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram shown in the lower part of FIG. The element is the sun gear Sm1 of the first planetary gear 51, the second element is the first coupling bodies Cm1 and Rm2, the third element is the second coupling bodies Rm1 and Cm2, and the fourth element is the sun gear Sm2 of the second planetary gear 52. Note that the first planetary gear 51 has a gear ratio j1 and the second planetary gear 52 has a gear ratio j2, and the vertical line Y2 where the sun gear Sm1 of the first planetary gear 51 is located and the vertical line Y3 where the first coupling bodies Cm1 and Rm2 are located. And the distance between the vertical line Y3 and the vertical line Y4 where the second coupling bodies Rm1 and Cm2 are located, and the distance between the vertical line Y4 and the vertical line Y5 where the sun gear Sm2 of the second planetary gear 52 is located Is set to j1: 1: j2.

  In the second embodiment, the sun gear Sm1 (first element) of the first planetary gear 51 and the carrier Cf (sixth element) of the speed reduction planetary gear 4 are coupled, and the second coupling bodies Rm1, Cm2 (third element) are coupled. It is connected to the output gear 3. The input shaft 2 is connected to the first coupling bodies Cm1, Rm2 (second element) via the second clutch C2, and the sun gear Sm2 (fourth element) of the second planetary gear 52 is connected via the third clutch C3. Further, the first coupling bodies Cm1 and Rm2 (second element) are coupled to the ring gear Rf (seventh element) of the speed reduction planetary gear 4 via the fourth clutch C4. Other configurations are the same as those in the first embodiment.

  In the second embodiment as well, eight forward speeds and one reverse speed are shifted, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, if the gear ratio i of the speed reduction planetary gear 4 is set to 1.3, the gear ratio j1 of the first planetary gear 51 is set to 1.4, and the gear ratio j2 of the second planetary gear 52 is set to 2.5, the gear ratio of each gear stage is set. Is the same as that shown in FIG.

  In the first embodiment, the speed reduction planetary gear 4 is a single pinion type planetary gear. However, as in the third embodiment shown in FIG. 5 and the fourth embodiment shown in FIG. The planetary gear 4 is a double-pinion type single planetary gear that is configured to support a pair of pinions Pf and Pf ′ that mesh with each other and one meshes with the sun gear Sf and the other mesh with the ring gear Rf so as to rotate and revolve by the carrier Cf. It is also possible to configure.

  Here, the three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the speed reduction planetary gear 4 of the third embodiment are arranged in the order from the left side in the order corresponding to the gear ratio in the speed diagram shown in the upper part of FIG. Assuming that the element is the sixth element and the seventh element, the fifth element is the sun gear Sf, the sixth element is the ring gear Rf, and the seventh element is the carrier Cf. The gear ratio of the speed reduction planetary gear 4 is i, and the ratio of the distance between the sun gear Sf and the ring gear Rf and the distance between the ring gear Rf and the carrier Cf is set to i−1: 1. Then, when the rotational speed of the sun gear Sf is “1” and the rotational speed of the carrier Cf is “0”, the output speed (the rotational speed of the ring gear Rf) N1 of the deceleration planetary gear 4 is 1 / i.

  In the third embodiment, the ring gear Rf (sixth element) of the speed reduction planetary gear 4 is connected to the first sun gear Sml (first element) of the speed change compound planetary gear 5, and the carrier Cr (seventh speed) of the speed reduction planetary gear 4 is connected. Element) is connectable to the carrier Cm (second element) of the shift type planetary gear 5 via the fourth clutch C4, and can be fixed to the transmission case 1 via the second brake B2. Other configurations are the same as those in the first embodiment. In the third embodiment as well, eight forward speeds and one reverse speed are changed, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, the gear ratio i of the speed reduction planetary gear 4 is 2.3, the gear ratio j1 of the ring gear Rm and the first sun gear Sml of the transmission double planetary gear 5 is 1.4, the ring gear Rm and the second sun gear Sms of the double planetary gear 5 for speed change. When the gear ratio j2 is set to 3.5, the gear ratios of the respective speeds are the same as those shown in FIG.

  Three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the planetary gear 4 for speed reduction according to the fourth embodiment are arranged in the order corresponding to the gear ratio in the speed diagram shown in the upper part of FIG. Assuming the sixth element and the seventh element, the fifth element is the carrier Cf, the sixth element is the ring gear Rf, and the seventh element is the sun gear Sf. The gear ratio of the planetary gear 4 for reduction is i, and the ratio of the distance between the carrier Cf and the ring gear Rf and the distance between the ring gear Rf and the sun gear Sf is set to 1: i-1. Then, when the rotational speed of the carrier Cf is “1” and the rotational speed of the sun gear Sf is “0”, the output speed (the rotational speed of the ring gear Rf) N1 of the deceleration planetary gear 4 is 1 / i.

  In the fourth embodiment, the ring gear Rf (sixth element) of the speed reduction planetary gear 4 is connected to the first sun gear Sml (first element) of the speed-changing planetary gear 5, and the carrier Cf (fifth speed) of the speed reduction planetary gear 4 is connected. Element) can be connected to the input shaft 2 via the first clutch C1, and can be fixed to the transmission case 1 via the first brake B1, and the sun gear Sf (seventh element) of the planetary gear 4 for speed reduction. ) Can be connected to the carrier Cm (second element) of the shift type planetary gear 5 via the fourth clutch C4, and can be fixed to the transmission case 1 via the second brake B2. Other configurations are the same as those in the first embodiment. In the fourth embodiment as well, eight forward speeds and one reverse speed are changed, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, the gear ratio i of the speed reduction planetary gear 4 is 1.769, the gear ratio j1 of the ring gear Rm and the first sun gear Sml of the transmission double planetary gear 5 is 1.4, the ring gear Rm and the second sun gear Sms of the double planetary gear 5 for speed change. When the gear ratio j2 is set to 3.5, the gear ratios of the respective speeds are the same as those shown in FIG.

  In the second embodiment, the speed reduction planetary gear 4 can be constituted by a double pinion type single planetary gear as in the third and fourth embodiments.

  Further, in the first to fourth embodiments, the second and third clutches C2 and C3, the output gear 3, the shift compound planetary gear 5, and the fourth clutch are sequentially arranged around the input shaft 2 from one end side. This is an automatic transmission for an FF vehicle in which C4, a planetary gear 4 for deceleration and a second brake B2, and a first clutch C1 and a first brake B1 are arranged. The same applies to an automatic transmission for an FR vehicle. The invention can be applied. For example, as in the fifth embodiment shown in FIG. 9, the first clutch C1 and the first brake B1, the deceleration planetary gear 4 and the second brake B2 around the input shaft 2 in this order from the one end (front end) side. The fourth clutch C4, the shifting double planetary gear 5, and the second and third clutches C2 and C3 are arranged, and the propeller shaft is an output member extending rearward of the ring gear Rm (third element) of the shifting double planetary gear 5. You may connect 3 '. In the fifth embodiment, the transmission of the first embodiment is changed to that for an FR vehicle, but the transmissions of the second to fourth embodiments can be similarly changed to those for an FR vehicle.

  Next, a sixth embodiment shown in FIG. The sixth embodiment includes a speed-changing planetary gear 5 similar to that of the first embodiment, and includes a speed-reducing planetary gear 6 instead of the speed-reducing planetary gear 4 of the first embodiment.

  The reduction type planetary gear 6 includes a sun gear Sf1, a ring gear Rf1, a first reduction planetary gear 61 having a carrier Cf1 that supports the sun gear Sf1 and the pinion Pf1 meshing with the ring gear Rf1, and a sun gear Sf2. , Using a second planetary gear 62 for reduction having a ring gear Rf2 and a carrier Cf2 that supports the pinion Pf2 meshing with the sun gear Sf2 and the ring gear Rf2 so as to rotate and revolve freely, and the carrier Cf1 of the first planetary gear 61 for reduction and the reduction The ring gear Rf2 of the second planetary gear 62 is connected to the ring gear Rf1 of the first planetary gear 61 for reduction and the carrier Cf2 of the second planetary gear 62 for reduction is connected.

  The double planetary gear 6 for reduction includes a sun gear Sf1 of the first planetary gear 61 for reduction, a sun gear Sf2 of the second planetary gear 62 for reduction, a carrier Cf1 of the first planetary gear 61 for reduction, and a ring gear Rf2 of the second planetary gear 62 for reduction. And four rotating elements comprising a connecting body (second connecting body) of the ring gear Rf1 of the first planetary gear 61 for reduction and the carrier Cf2 of the second planetary gear 62 for reduction. become. Then, if these rotating elements are the fifth element, the sixth element, the seventh element, and the eighth element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram shown in the upper part of FIG. The elements are the sun gear Sf1 of the first planetary gear 61 for reduction, the second element is the first coupling bodies Cf1 and Rf2, the third element is the second coupling bodies Rf1 and Cf2, and the fourth element is the sun gear Sf2 of the second planetary gear 62 for reduction. Become. The gear ratio of the first planetary gear for reduction 61 is i1, the gear ratio of the second planetary gear for reduction 62 is i2, and the distance between the sun gear Sf1 of the first planetary gear for reduction 61 and the first coupling bodies Cf1 and Rf2 is The ratio between the interval between the first connector Cf1, Rf2 and the second connector Rf1, Cf2 and the interval between the second connector Rf1, Cf2 and the sun gear Sf2 of the second planetary gear 62 for reduction is set to i1: 1: i2. Has been. Then, when the rotational speed of the sun gear Sf1 of the first planetary gear for deceleration 61 is “1” and the rotational speed of the second coupling bodies Rf1 and Cf2 is “0”, the output speed of the double planetary gear for deceleration 6 (the first coupling body Cf1). , Rf2) N1 becomes 1 / (i1 + 1), the rotation speed of the sun gear Sf1 of the first planetary gear 61 for reduction is “1”, and the rotation speed of the sun gear Sf2 of the second planetary gear 62 for reduction is “0”. The output speed N2 of the double planetary gear 6 for deceleration is (i2 + 1) / (i1 + i2 + 1).

  In the sixth embodiment, the first sun gear Sml (first element) of the double planetary gear 5 for transmission and the first coupling bodies Cf1 and Rf2 (sixth element) are coupled and the sun gear Sf1 (first gear gear 61 for deceleration) ( The fifth element) can be connected to the input shaft 2 via the first clutch C1. Further, the sun gear Sf2 (eighth element) of the second planetary gear 62 for deceleration can be freely connected to the carrier Cm (second element) of the compound planetary gear 5 for speed change via the fourth clutch C4, and the second brake B2 is provided. The second connecting bodies Rf1 and Cf2 (seventh element) can be fixed to the transmission case 1 via the first brake B1. Other configurations are the same as those in the first embodiment.

  The first coupling bodies Cf1 and Rf2 are always located on the same vertical line Y2 as the first sun gear Sml of the transmission double planetary gear 5 in the speed diagram of the transmission double planetary gear 5 shown in the lower part of FIG. Further, when the fourth clutch C4 is engaged, the sun gear Sf2 of the second planetary gear 62 for reduction is positioned on the same vertical line Y4 as the carrier Cm of the double planetary gear 5 for transmission, and the second coupling bodies Rf1 and Cf2 are vertically The sun gear Sf1 of the first planetary gear 61 for speed reduction is located from the vertical line Y2 to the vertical line Y2 and is located on the vertical line Y3 that is 1 / (1 + i2) of the distance between the vertical line Y2 and the vertical line Y4 from the line Y2. It is located on the vertical line Y1 that is separated to the left by i1 times the interval between the vertical lines Y3. Note that the gear ratio between the ring gear Rm and the first sun gear Sml of the double planetary gear 5 for shifting is j1, the gear ratio between the ring gear Rm and the second sun gear Sms is j2, and the ring gear Rm of the double planetary gear 5 for shifting is from the vertical line Y4. The second sun gear Sms of the double planetary gear 5 for shifting is located between the vertical line Y5 and the vertical line Y4 and the vertical line Y5, located on the vertical line Y5 that is separated to the right by 1 / j1 of the interval between the vertical line Y2 and the vertical line Y4. Is located on the vertical line Y6 that is separated to the right by (j2-1) times the interval of.

  In the sixth embodiment, when the third clutch C3, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y4 is “0”, and the rotational speed at the vertical line Y6 is “1”. ”And the rotation speed along the vertical line Y5 is“ 1st ”. That is, the first gear is established.

  When the third clutch C3, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y3 becomes “0”, the rotational speed at the vertical line Y6 becomes “1”, and the vertical line Y5 The rotation speed at is 2nd. That is, the second gear is established.

  When the third clutch C3, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y6 is "1", and the vertical line Y5 The rotation speed at is “3rd”. That is, the third gear is established.

  When the first clutch C1, the third clutch C3, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y6 is “1”, and the vertical line Y5 The rotation speed is “4th”. That is, the fourth gear is established.

  When the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N2, the rotational speed at the vertical line Y6 is “1”, and the rotational speed at the vertical line Y5 is The rotation speed is “5th”. That is, the fifth gear is established.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed at the vertical line Y4 and the rotational speed at the vertical line Y6 are both “1”, and the rotational speed at the vertical line Y5 is also “1”. "6th". That is, the sixth gear is established. Even if the first clutch C1 is engaged, the sixth gear is established by engaging the second clutch C2 and the third clutch C3.

  When the first clutch C1, the second clutch C2, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N2, the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed is “7th”. That is, the seventh gear is established.

  When the first clutch C1, the second clutch C2, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed is “8th”. That is, the eighth gear is established.

  When the second clutch C2, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed at is “9th”. That is, the ninth gear is established.

  When the second clutch C2, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y3 is "0", the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed at is “10th”. That is, the 10th gear is established.

  When the first clutch C1, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N2, the rotational speed at the vertical line Y4 is "0", and the vertical line Y5 The rotation speed becomes negative “Rev1”. That is, the first reverse speed is established.

  When the first clutch C1, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “0”, and the vertical line Y5 The rotation speed is negative “Rev2”. That is, the second reverse speed is established.

  FIG. 10B is a diagram summarizing the relationship between the above-described shift speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2, and ◯ represents engagement. In the sixth embodiment, it is possible to perform shifts of 10 forward speeds and 2 reverse speeds. And since three engagement elements engage in each gear stage among the six engagement elements, the number of engagement elements released in each gear stage is three as in the above embodiment. Compared to the conventional example in which the four engagement elements are released, the friction loss due to the released engagement elements can be reduced, and the efficiency of the transmission is improved.

  FIG. 10B shows the above-described cases where the gear ratios i1, i2, j1, and j2 are i1 = 2.0, i2 = 1.4, j1 = 1.6, and j2 = 3.5, respectively. The gear ratio of the shift speed (the rotational speed of the input shaft 2 / the rotational speed of the output gear 3) is also shown. According to this, the common ratio (ratio of gear ratios between gears) becomes appropriate, and the range (first speed ratio / 10 speed ratio) becomes appropriate.

  By the way, in the sixth embodiment, the double planetary gear 6 for reduction is configured by combining the two planetary gears 61 and 62 composed of a single planetary gear. However, as in the seventh embodiment shown in FIG. 12, the double planetary gear 6 for reduction is used. As shown, the first sun gear Sfl, the second sun gear Sfs, the ring gear Rf, the first pinion Pfl that meshes with the first sun gear Sfl and the ring gear Rf, the second sun gear Sfs, and the second pinion that meshes with the first pinion Pfl. A Ravigneaux type planetary gear having a carrier Cf that supports Pfs in a freely rotating and revolving manner may be used.

  Four rotating elements including the first sun gear Sfl, the second sun gear Sfs, the ring gear Rf, and the carrier Cf of the double planetary gear 6 for speed reduction are arranged in an order corresponding to the gear ratio in the speed diagram shown in the upper part of FIG. Assuming the fifth element, the sixth element, the seventh element, and the eighth element from the left side, the fifth element is the first sun gear Sfl, the sixth element is the carrier Cf, the seventh element is the ring gear Rf, and the eighth element is the second element. It becomes the sun gear Sfs. The gear ratio between the ring gear Rf and the first sun gear Sfl is i1, the gear ratio between the ring gear Rf and the second sun gear Sfs is i2, and the distance between the first sun gear Sfl and the carrier Cf and between the carrier Cf and the ring gear Rf. The ratio of the interval and the interval between the ring gear Rf and the second sun gear Sms is set to i1: 1: i2-1.

  In the seventh embodiment, the carrier Cf (sixth element) of the double planetary gear 6 for reduction and the first sun gear Sml (first element) of the double planetary gear 5 for transmission are connected, and the first sun gear of the double planetary gear 6 for reduction is connected. Sf1 (fifth element) is coupled to the input shaft 2 via the first clutch C1. Further, the second sun gear Sfs (eighth element) of the double planetary gear for deceleration 6 can be connected to the carrier Cm (second element) of the double planetary gear for shifting 5 via the fourth clutch C4, and the second brake B2 The ring gear Rf (seventh element) of the speed reduction double planetary gear 6 can be fixed to the transmission case 1 via the first brake B1. Other configurations are the same as those of the sixth embodiment.

  In the seventh embodiment as well, 10 forward speeds and 2 reverse speeds are changed, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, the gear ratio i1 between the ring gear Rf and the first sun gear Sfl of the reduction double planetary gear 6 is 2.0, the gear ratio i2 between the ring gear Rf and the second sun gear Sfs of the reduction double planetary gear 6 is 2.4, and the gear change double planetary gear. When the gear ratio j1 between the ring gear Rm 5 and the first sun gear Sml is set to 1.6, and the gear ratio j2 between the ring gear Rm and the second sun gear Sms of the transmission double planetary gear 5 is set to 3.5, the gear ratio of each gear stage is as shown in FIG. This is the same as that shown in 10 (b).

  By the way, in the sixth and seventh embodiments, the speed-changing planetary gear 5 is constituted by a Ravigneaux-type planetary gear. However, the speed-changing planetary gear 5 of the sixth and seventh embodiments is similar to that of the second embodiment. It is also possible to change to a double planetary gear configured by combining two single planetary gears. Moreover, although the sixth and seventh embodiments are automatic transmissions for FF vehicles, the present invention can be similarly applied to automatic transmissions for FR vehicles. For example, as in the eighth embodiment shown in FIG. 14, the first clutch C1, the speed-reducing planetary gear 6 and the first brake B1, and the second brake B2 are sequentially arranged around the input shaft 2 from one end (front end) side. And the fourth clutch C4, the shift type planetary gear 5, and the second and third clutches C2 and C3, and the propeller shaft as an output member extending backward from the ring gear Rm (third element) of the shift type planetary gear 5 You may connect 3 '. In the eighth embodiment, the transmission of the sixth embodiment is changed to that for an FR vehicle, but the transmission of the seventh embodiment can be changed to that for an FR vehicle as well.

(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 planetary gear for deceleration of the 1st Embodiment and the compound planetary gear for gear shifting. The skeleton figure of 2nd Embodiment of this invention transmission. The speed diagram of the planetary gear for deceleration of the 2nd Embodiment and the compound planetary gear for transmission. The skeleton figure of 3rd Embodiment of this invention transmission. The speed diagram of the planetary gear for deceleration of the 3rd Embodiment and the compound planetary gear for transmission. The skeleton figure of 4th Embodiment of this invention transmission. The speed diagram of the planetary gear for deceleration of the 4th Embodiment and the compound planetary gear for gear shifting. The skeleton figure of 5th Embodiment of this invention transmission. (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 double planetary gear for deceleration and the double planetary gear for speed change of 6th Embodiment. The skeleton figure of 7th Embodiment of this invention transmission. The speed diagram of the double planetary gear for deceleration and the double planetary gear for speed change of 7th Embodiment. The skeleton figure of 8th Embodiment of this invention transmission.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft (input member), 3 ... Output gear (output member), 3 '... Propeller shaft (output member), 4 ... Reduction planetary gear, Sf ... Sun gear of reduction planetary gear (1st Fifth element in the embodiment), Cf ... Deceleration planetary gear carrier (sixth element in the first embodiment), Rf ... Deceleration planetary gear ring gear (seventh element in the first embodiment), 5 ... Shifting planetary gear , Sml: first sun gear (first element in the first embodiment) of the double planetary gear for shifting, Sms: second sun gear (fourth element in the first embodiment) of the double planetary gear for shifting, Cm: of the double planetary gear for shifting Carrier (second element in the first embodiment), Rm ... ring gear of the double planetary gear for shifting (in the first embodiment , 6 ... deceleration double planetary gear, Sfl ... first sun gear of the reduction double planetary gear (fifth element in the seventh embodiment), Sfs ... second sun gear of the reduction planetary gear (in the seventh embodiment) Eighth element), Cf... Reduction planetary gear carrier (sixth element in the seventh embodiment), Rf... Reduction double planetary gear ring gear (seventh element in the seventh embodiment), C1. 1 engagement element), C2 ... 2nd clutch (2nd engagement element), C3 ... 3rd clutch (3rd engagement element), C4 ... 4th clutch (4th engagement element), B1 ... 1st brake (5th engagement element), B2 ... 2nd brake (6th engagement element).

Claims (2)

An automatic transmission that shifts the rotation of an input member to a plurality of stages via a speed reduction planetary gear and a speed change planetary gear arranged in a transmission case, and transmits them to an output member.
The dual planetary gear for shifting has four rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the order of arrangement in the speed diagram, respectively, the first element, the second element, the third element, and the second element. The four elements, and the three elements consisting of the sun gear, ring gear, and carrier of the planetary gear for reduction, are arranged as the fifth element, the sixth element, and the seventh element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The element and the sixth element are coupled, and the third element is coupled to the output member;
A first engagement element switchable between a state of connecting the input member and the fifth element and a state of disconnecting the connection;
A second engagement element switchable between a state of connecting the input member and the second element and a state of disconnecting the connection;
A third engagement element switchable between a state of connecting the input member and the fourth element and a state of disconnecting the connection;
A fourth engagement element that is switchable between a state of connecting the second element and the seventh element and a state of disconnecting the connection;
A fifth engagement element switchable between a state in which the fifth element is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising a sixth engagement element that is switchable between a state in which the seventh element is fixed to the transmission case and a state in which the fixation is released. An automatic transmission that shifts the rotation of an input member to a plurality of stages via a speed reduction compound planetary gear and a speed change compound planetary gear that are arranged in a transmission case and transmits them to an output member.
Each of the planetary gears for shifting and decelerating has four rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and each of the four rotating elements of the shifting planetary gear is arranged in the order of arrangement in the speed diagram. Element, second element, third element and fourth element, and the four rotating elements of the speed reduction compound planetary gear in the order of arrangement in the velocity diagram as the fifth element, sixth element, seventh element and eighth element, respectively. The first element and the sixth element are connected, and the third element is connected to the output member,
A first engagement element switchable between a state of connecting the input member and the fifth element and a state of disconnecting the connection;
A second engagement element switchable between a state of connecting the input member and the second element and a state of disconnecting the connection;
A third engagement element switchable between a state of connecting the input member and the fourth element and a state of disconnecting the connection;
A fourth engagement element that is switchable between a state of connecting the second element and the eighth element and a state of disconnecting the connection;
A fifth engagement element switchable between a state in which the seventh element is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising a sixth engaging element that is switchable between a state in which the eighth element is fixed to the transmission case and a state in which the fixation is released.

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