JP2009185862A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission including a single planetary gear, a double planetary gear and six engagement elements, capable of engaging three of the engagement elements at every gear stage so as to reduce friction loss caused by the engagement elements being disengaged. <P>SOLUTION: Four elements of the double planetary gear 4 are shown as first, second, third and fourth elements in the order of their arrangement in the speed diagram, and three elements of the single planetary gear 5 are shown as fifth, sixth and seventh elements in the order of their arrangement in the speed diagram. The third elements Rf, Cm are connected to the fifth element Rr and the sixth element Cr is connected to an output member 3. As the six engagement elements, there are provided first, second and third engagement elements C1, C2 and C3 for respectively connecting an input member 2 to the first element Sf, the second elements Cf, Sm and the seventh element Sr, a fourth engagement element C4 for connecting the fourth element Rm to the sixth element Cr, a fifth engagement element B1 for fixing the first element Sf and a sixth engagement element B2 for fixing the second elements Cf, Sm. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an automatic transmission capable of multi-stage shifting using a planetary gear.

  Conventionally, Patent Document 1 discloses an automatic transmission that can perform a forward seven-speed shift using a single planetary gear on the input side, a double planetary gear on the output side, and six engagement elements. Yes. In this structure, the double planetary gear 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 rotation element configured by connecting a sun gear of one planetary gear and a carrier of the other planetary gear, and a second rotation configured by connecting a carrier of one planetary gear and a ring gear of the other planetary gear. An element, a third rotating element composed of a ring gear of one planetary gear, and a fourth rotating element composed 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.

  In addition, as an engagement element, the rotation of the input member is decelerated by a single planetary gear and transmitted to the fourth rotation element, and the first clutch which can be switched between a state where this transmission is cut off and the rotation of the input member by a single planetary gear. A second clutch that can be switched between a state in which it is decelerated and transmitted to the first rotating element and a state in which this transmission is cut off, a state in which the input member and the second rotating element are connected, and a state in which this connection is cut off. 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 third and fourth clutches are engaged. The fifth gear is established by engaging, the sixth gear is established by engaging the second clutch and the third clutch, and the seventh gear is established by engaging the third clutch and the first brake. Is established.
JP2003-130152A (FIGS. 7 and 8)

  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 problems, the present invention shifts the rotation of an input member to a plurality of stages via an input-side compound planetary gear and an output-side single planetary gear arranged in the transmission case, and transmits them to the output member. In the automatic transmission, the compound planetary gear 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, a first element, a second element, As the third element and the fourth element, the three elements consisting of the sun gear, the ring gear, and the carrier of the single planetary gear are arranged in the order corresponding to the gear ratio in the speed diagram in the order of arrangement, respectively, the fifth element, the sixth element, and the seventh element. The third element and the fifth element are connected, the sixth element is connected to the output member, and the rotation of the input member is transmitted to the first element and the transmission is cut off. A switchable first engagement element, a second engagement element switchable between a state in which the rotation of the input member is transmitted to the second element and a state in which the transmission is cut off, and a rotation of the input member are transmitted to the seventh element A third engagement element that can be switched between a state to be disconnected and a state to cut off this transmission, a fourth engagement element that is switchable between a state to connect the fourth element and the sixth element and a state to disconnect this connection, A fifth engaging element that can be switched between a state in which the first element is fixed to the transmission case and a state in which the fixing is released; a state in which the second element is fixed to the transmission case; and a state in which the fixing is released And a switchable sixth engaging element.

  According to the present invention, as will be apparent from the description of the embodiment described later, it is possible to perform seven forward shifts and three of the first to sixth engaging elements at each shift step. The engaging elements are engaged. Therefore, 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.

  In the present invention, a reduction planetary gear is provided in addition to the double planetary gear and the single planetary gear so that the rotation of the input member is decelerated by the reduction planetary gear and transmitted to the first element when the first engagement element is engaged. Alternatively, if the rotation of the input member is decelerated by the reduction planetary gear and transmitted to the seventh element when the third engagement element is engaged, a forward 10-speed shift can be performed.

  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).

  In the transmission case 1, an input-side planetary gear 4 and an output-side single planetary gear 5 are disposed around the input shaft 2. The compound planetary gear 4 includes a first planetary gear 41 having 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 rotate and revolve, a sun gear Sm, and a ring gear Rm. The second planetary gear 42 having a carrier Cm that supports the pinion Pm meshing with the sun gear Sm and the ring gear Rm so as to rotate and revolve freely, and the carrier Cf of the first planetary gear 41 and the sun gear Sm of the second planetary gear 42 are connected. In addition to being connected, the ring gear Rf of the first planetary gear 41 and the carrier Cm of the second planetary gear 42 are connected.

  The double planetary gear 4 includes a sun gear Sf of the first planetary gear 41, a ring gear Rm of the second planetary gear 42, a coupling body (first coupling body) of the carrier Cf of the first planetary gear 41 and the sun gear Sm of the second planetary gear 42. The first planetary gear 41 has four rotating elements including the ring gear Rf of the first planetary gear 41 and the coupling body (second coupling body) of the carrier Cm of the second planetary gear 42. These rotational elements are arranged from the left in the order in which they are arranged at intervals corresponding to the gear ratios in the speed diagram shown in the upper part of FIG. 2 (the rotational speeds of the plurality of rotational elements constituting the planetary gear can be represented by straight lines). Assuming that the first element, the second element, the third element, and the fourth element, respectively, the first element is the sun gear Sf of the first planetary gear 41, the second element is the first coupling body Cf, Sm, and the third element is the second coupling. The bodies Rf and Cm and the fourth element become the ring gear Rm of the second planetary gear 42. The gear ratio of the first planetary gear 41 (the number of teeth of the ring gear Rf / the number of teeth of the sun gear Sf) is i, and the gear ratio of the second planetary gear 42 (the number of teeth of the ring gear Rm / the number of teeth of the sun gear Sm) is j. The distance between the sun gear Sf of the first planetary gear 41 and the first coupling bodies Cf, Sm, the spacing between the first coupling bodies Cf, Sm and the second coupling bodies Rf, Cm, the second coupling bodies Rf, Cm and the second planetary gear. The ratio with the interval between the 42 ring gears Rm is set to i: 1: 1 / j.

  Here, the lower horizontal line and the upper horizontal line of the speed diagram indicate that the rotational speeds are “0” and “1” (the same rotational speed as the input shaft 2), respectively. When the first clutch C1 and the second brake B2, which will be described later, are engaged, the rotation speed of the sun gear Sf of the first planetary gear 41 is "1", and the rotation speed of the first coupling bodies Cf, Sm is "0". The rotational speed of the two connected bodies Rf, Cm is N1, the rotational speed of the sun gear Sf of the first planetary gear 41 is “0” due to the engagement of the second clutch C2 and the first brake B1, which will be described later, and the first connected bodies Cf, Sm When the rotation speed of the second coupling bodies Rf and Cm when the rotation speed becomes “1” is N2, N1 = −1 / i and N2 = 1 + 1 / i.

  The single planetary gear 5 includes a sun gear Sr, a ring gear Rr, and a carrier Cr that supports the pinion Pr that meshes with the sun gear Sr and the ring gear Rr so as to freely rotate and revolve. Referring to the velocity diagram of single planetary gear 5 shown in the lower part of FIG. 2, the three elements of sun gear Sr, ring gear Rr and carrier Cr of single planetary gear 5 are arranged at intervals corresponding to the gear ratio in the velocity diagram. If the fifth element, the sixth element, and the seventh element are sequentially arranged from the left side, the fifth element is the ring gear Rr, the sixth element is the carrier Cr, and the seventh element is the sun gear Sr. If the gear ratio of the single planetary gear 5 (the number of teeth of the ring gear Rr / the number of teeth of the sun gear Sr) is k, the distance between the ring gear Rr (vertical line Y3) and the carrier Cr (vertical line Y4) and the carrier Cr (vertical line). The ratio between Y4) and the distance between the sun gear Sr (vertical line Y5) is 1: k.

  Here, in the present embodiment, the second coupling bodies Rf, Cm (third element) of the double planetary gear 4 and the ring gear Rr (fifth element) of the single planetary gear 5 are coupled, and the carrier Cr (first) of the single planetary gear 5 is coupled. 6 elements) are connected to the output gear 3. Further, as the engagement element, a first engagement that can be switched between a state in which the rotation of the input shaft 2 is transmitted to the sun gear Sf (first element) of the first planetary gear 41 constituting the double planetary gear 4 and a state in which the transmission is cut off. The first clutch C1, which is an element, and a second engagement element that can be switched between a state in which the rotation of the input shaft 2 is transmitted to the first coupling body Cf, Sm (second element) of the double planetary gear 4 and a state in which the transmission is cut off. A second clutch C2 as a third, and a third clutch C3 as a third engagement element that can be switched between a state in which the rotation of the input shaft 2 is transmitted to the sun gear Sr (seventh element) of the single planetary gear 5 and a state in which this transmission is cut off. A state in which the ring gear Rm (fourth element) of the second planetary gear 42 constituting the compound planetary gear 4 and the carrier Cr (sixth element) of the single planetary gear 5 are connected and a state in which this connection is broken. A state in which the fourth clutch C4, which is a switchable fourth engagement element, and the sun gear Sf (first element) of the first planetary gear 41 constituting the double planetary gear 4 are fixed to the transmission case 1 and a state in which this fixing is released. The first brake B1, which is a fifth engaging element that can be switched to the first, and the first coupling body Cf, Sm (second element) of the double planetary gear 4 are fixed to the transmission case 1 and the fixed state is released. And a second brake B2 which is a switchable sixth engaging element.

  Here, by connecting the second coupling bodies Rf, Cm of the double planetary gear 4 and the ring gear Rr of the single planetary gear 5, the second coupling bodies Rf, Cm of the single planetary gear 5 are shown in the lower speed diagram of FIG. It is always located on the same vertical line Y3 as the ring gear Rr. Further, when the fourth clutch C4 is engaged, the ring gear Rm of the second planetary gear 42 constituting the double planetary gear 4 is positioned on the same vertical line Y4 as the carrier Cr of the single planetary gear 5. And the 1st coupling body Cf and Sm of the compound planetary gear 4 are located on the vertical line Y2 which left | separated from the vertical line Y3 to the left side only j times the space | interval between the vertical line Y3 and the vertical line Y4, and comprise the compound planetary gear 4 The sun gear Sf of the first planetary gear 41 is positioned on the vertical line Y1 that is separated from the vertical line Y2 to the left by i times the interval between the vertical line Y2 and the vertical line Y3.

  In the present embodiment, when the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotational speed at the vertical line Y3 is N1, and the rotational speed at the vertical line Y5 is “1”. The rotational speed of the single planetary gear 5 connected to the output gear 3 along the vertical line Y4 where the carrier Cr 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 speeds of all the rotating elements of the compound planetary gear 4 become “0”, so the rotational speed at the vertical line Y3 is “0”. ”, The rotational speed at the vertical line Y5 is“ 1 ”, and the rotational speed at the vertical line Y4 is“ 2nd ”. That is, the second gear is established.

  When the third clutch C3, the fourth clutch C4, 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 “3rd”. That is, the third 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 “4th”. That is, the fourth gear is established.

  When the second clutch C2, the third clutch C3, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y2 and the rotational speed at the vertical line Y5 are both "1", and the vertical line Y4 The rotation speed is also “1”, “5th”. That is, the fifth gear is established. Note that the fifth speed is established even when the first clutch C1 is engaged in addition to the second, third, and fourth clutches C2, C3, and C4.

  When the second clutch C2, the third clutch C3, and the first brake B1 are engaged, the rotational speed at the vertical line Y3 is N2, the rotational speed at the vertical line Y5 is "1", and the vertical line Y4 The rotation speed is “6th”. That is, the sixth gear is established.

  When the second clutch C2, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y1 is “0”, the rotational speed at the vertical line Y3 is N2, and the vertical line Y4 The rotation speed is “7th”. That is, the seventh 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 Y1 is “1”, the rotational speed at the vertical line Y3 is N1, and the vertical line Y4 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 clutch C1 at the fifth speed stage indicates that the first clutch C1 may or may not be engaged.

  FIG. 1B shows the gear ratio (input shaft 2) for each gear position when the gear ratios i, j, k described above are i = 3.2, j = 2.0, and k = 1.4, 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 total range (first speed ratio / 7th 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 first embodiment, the single planetary gear 5 is constituted by a single pinion type. However, as in the second embodiment shown in FIG. 3 and the third embodiment shown in FIG. A pair of pinions Pr and Pr 'meshing with each other and one meshing with the sun gear Sr and the other meshing with the ring gear Rr may be constituted by a double pinion type that is supported by a carrier Cr so as to be able to rotate and revolve. Is possible.

  Here, the three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the single planetary gear 5 of the second embodiment are changed from the left side in the order corresponding to the gear ratio in the speed diagram shown in the lower part of FIG. When the sixth element and the seventh element are used, the fifth element is a carrier Cr, the sixth element is a ring gear Rr, and the seventh element is a sun gear Sr. The gear ratio of the single planetary gear 5 is k, and the distance between the carrier Cr (vertical line Y3) and the ring gear Rr (vertical line Y4) and the distance between the ring gear Rr (vertical line Y4) and the sun gear Sr (vertical line Y5) are shown. The ratio is set to 1: k-1.

  In the second embodiment, the second rotating bodies Rf, Cm (third element) of the double planetary gear 4 and the carrier Cr (fifth element) of the single planetary gear 5 are coupled, and the ring gear Rr (sixth element) of the single planetary gear 5 is connected. Element) is connected to the output gear 3 and is connected to the ring gear Rm (fourth element) of the second planetary gear 42 constituting the double 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, seven forward gears and one reverse gear shift are performed, and the relationship between the gears and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same.

  Three elements including the sun gear Sr, the ring gear Rr, and the carrier Cr of the single planetary gear 5 of the third embodiment are arranged in the order corresponding to the gear ratio in the speed diagram shown in the lower part of FIG. Assuming the elements and the seventh element, the fifth element is the sun gear Sr, the sixth element is the ring gear Rr, and the seventh element is the carrier Cr. The gear ratio of the single planetary gear 4 is k, and the distance between the sun gear Sr (vertical line Y3) and the ring gear Rr (vertical line Y4), and the distance between the ring gear Rr (vertical line Y4) and the carrier Cr (vertical line Y5). The ratio is set to k-1: 1.

  In the third embodiment, the second rotating bodies Rf and Cm (third element) of the double planetary gear 4 and the sun gear Sr (fifth element) of the single planetary gear 5 are connected, and the ring gear Rr (sixth element) of the single planetary gear 5 is connected. Element) is connected to the output gear 3, and is connected to the ring gear Rm (fourth element) of the second planetary gear 42 constituting the double planetary gear 4 via the fourth clutch C4. Further, the carrier Cr (single planetary gear 5) The seventh element) is coupled to the input shaft 2 via the third clutch C3. Other configurations are the same as those in the first embodiment. In the third embodiment as well, seven 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.

  In the first to third embodiments, the third clutch C3, the output gear 3, the single planetary gear 5, the double planetary gear 4, the fourth clutch C4, Although it is an automatic transmission for FF vehicles in which a two-clutch C2 and a second brake B2 and a first brake B1 and a first clutch C1 are arranged, the present invention can be similarly applied to an automatic transmission for an FR vehicle. . For example, as in the fourth embodiment shown in FIG. 7, the first clutch C1 and the first brake B1, the double planetary gear 4, the second brake B2, and the second clutch are sequentially arranged around the input shaft 2 from one end (front end) side. Two clutches C2, a fourth clutch C4, a single planetary gear 5, and a third clutch C3 are arranged, and a carrier Cr (third element) of the single planetary gear 5 is connected to a propeller shaft 3 'as an output member extending backward. May be. In the fourth embodiment, the transmission of the first embodiment is changed to that for an FR vehicle, but the transmissions of the second and third embodiments can also be changed to those for an FR vehicle.

  Next, a fifth embodiment shown in FIG. In the fifth embodiment, the speed reduction planetary gear 6 is added to the transmission of the first embodiment, and the rotation of the input shaft 2 is decelerated by the speed reduction planetary gear 6 when the first clutch C1 is engaged. This is transmitted to Sf (first element).

  The speed reduction planetary gear 6 includes a sun gear Sa, a ring gear Ra, and a carrier Ca that supports the pinion Pa meshing with the sun gear Sa and the ring gear Ra so as to be capable of rotating and revolving. The sun gear Sa is a fixed element that is fixed to the transmission case 1, the ring gear Ra is an input element that is connected to the input shaft 2, and the carrier Ca that is an output element is passed through the first clutch C1 to the sun gear Sf ( Connected to the first element). Other configurations are the same as those of the first embodiment.

  In the speed diagram of the speed reduction planetary gear 6 shown in the upper part of FIG. 9, the carrier Ca as an output element is located between the sun gear Sa and the ring gear Ra. The gear ratio of the planetary gear 6 for deceleration is m, and the ratio between the distance between the sun gear Sa and the carrier Ca and the distance between the carrier Ca and the ring gear Ra is set to m: 1. Then, the output speed (speed of rotation of the carrier Ca) N0 of the deceleration planetary gear 6 is m / (m + 1).

  Referring to the speed diagram of the compound planetary gear 4 shown in the middle of FIG. 9, the rotational speed of the sun gear Sf is N0 and the rotational speeds of the first coupling bodies Cf and Sm are engaged with the first clutch C1 and the second brake B2. N1 is the rotational speed of the second coupling body Rf, Cm when the rotational speed of the clutch is "0", and the rotational speed of the sun gear Sf is N0 due to the engagement of the first clutch C1 and the second clutch C2. When the rotational speed of Sm becomes “1”, the rotational speed of the second coupling body Rf, Cm is N2, and the rotational speed of the sun gear Sf is “0” due to the engagement between the first brake B1 and the second clutch C2. When the rotation speed of the second coupling body Rf, Cm when the rotation speed of the first coupling body Cf, Sm becomes “1” is N3, N1 = −N0 / i, N2 = 1 + (1-N0) / i, N3 = 1 + 1 / i.

  In the fifth embodiment, when the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotational speed at the vertical line Y3 is N1, and the rotational speed at the vertical line Y5 is “1”. The rotation speed at the vertical line Y4 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 speeds of all the rotating elements of the compound planetary gear 4 become “0”, so the rotational speed at the vertical line Y3 is “0”. ”, The rotational speed at the vertical line Y5 is“ 1 ”, and the rotational speed at the vertical line Y4 is“ 2nd ”. That is, the second gear is established.

  When the third clutch C3, the fourth clutch C4, 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 “3rd”. That is, the third 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 “4th”. That is, the fourth gear is established.

  When the first clutch C1, the third clutch C3, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y1 is N0, the rotational speed at the vertical line Y5 is “1”, and the rotational speed at the vertical line Y4 is The rotation speed is “5th”. That is, the fifth gear is established.

  When the second clutch C2, the third clutch C3, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y2 and the rotational speed at the vertical line Y5 are both "1", and the vertical line Y4 The rotational speed is also “6th” which is “1”. That is, the sixth gear is established.

  When the first clutch C1, the second clutch C2, and the third clutch C3 are engaged, the rotational speed at the vertical line Y3 is N2, the rotational speed at the vertical line Y5 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 third clutch C3, and the first brake B1 are engaged, the rotational speed at the vertical line Y3 is N3, the rotational speed at the vertical line Y5 is “1”, and the rotational speed at the vertical line Y4 is The rotation speed is “8th”. That is, the eighth gear is established.

  When the first clutch C1, the second clutch C2, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y1 becomes N0, the rotational speed at the vertical line Y3 becomes N2, and the rotational speed at the vertical line Y4. Becomes “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 Y1 is “0”, the rotational speed at the vertical line Y3 is N3, and the vertical line Y4 The rotation speed 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 Y1 is N0, the rotational speed at the vertical line Y3 is N1, and the rotational speed at the vertical line Y4. Becomes negative “Rev”. That is, the reverse gear is established.

  FIG. 8B 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. 8B, the gear ratio i of the first planetary gear 41 of the double planetary gear 4 is 2.2, the gear ratio j of the second planetary gear 42 is 1.5, and the gear ratio k of the single planetary gear 5 is 1.5. Also shown are the gear ratios of the respective speeds when the gear ratio m of the planetary gear 6 for reduction is 1.5. According to this, the common ratio becomes appropriate and the total range becomes appropriate.

  Also in the fifth 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. Become. 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 fifth embodiment, a single-pinion type gear is used as the speed reduction planetary gear 6, but as the speed reduction planetary gear 6 is engaged with each other and one of them is a sun gear Sa as in the sixth embodiment shown in FIG. Alternatively, a double pinion type in which a pair of pinions Pa and Pa ′, which are meshed with each other and meshed with the ring gear Ra, are supported by a carrier Ca so as to rotate and revolve freely may be used.

  Here, in the sixth embodiment, the sun gear Sa is a fixed element that is fixed to the transmission case 1, the carrier Ca is an input element that is connected to the input shaft 2, and the ring gear Ra that is an output element is interposed via the first clutch C1. Are connected to the sun gear Sf (first element) of the compound planetary gear 4, but the fixed element and the input element are replaced, and the sun gear Sa is fixed as the input element and the carrier Ca is fixed as in the seventh embodiment shown in FIG. It can also be an element.

  Further, in the fifth to seventh embodiments, the rotation of the input shaft 2 is decelerated by the speed reduction planetary gear 6 and is switched between the state in which the rotation is transmitted to the sun gear Sf (first element) of the compound planetary gear 4 and the state in which this transmission is released. The first clutch C1 that connects the output element of the speed reduction planetary gear 6 and the sun gear Sf of the double planetary gear 4 is used as the first engaging element that can be freely engaged. However, as in the eighth embodiment shown in FIG. It is also possible to use a third brake B3 that can be switched between a state in which the fixing element of the planetary gear 6 is fixed to the transmission case 1 and a state in which the fixing is released as the first engaging element. In the eighth embodiment, the sun gear Sa is a fixed element. However, when the carrier Ca is a fixed element as in the seventh embodiment, the first clutch C1 can be replaced by the third brake B3. is there.

  Further, in the transmission for the FR vehicle, as in the ninth embodiment shown in FIG. 13, the planetary gear for deceleration 6, the first clutch C <b> 1, and the first clutch are sequentially arranged around the input shaft 2 from one end (front end) side. Brake B1, double planetary gear 4, second brake B2 and second clutch C2, third clutch C3 and fourth clutch C4, and single planetary gear 5 are arranged, and propeller shaft that uses carrier Cr of single planetary gear 5 as an output member What is necessary is just to connect 3 '. In the ninth embodiment, the fifth embodiment is changed to an FR vehicle transmission, but the sixth to eighth embodiments can be changed to an FR vehicle transmission.

  Next, a tenth embodiment shown in FIG. In the tenth embodiment, a speed reduction planetary gear 6 is added to the transmission of the second embodiment, and when the third clutch C3 is engaged, the rotation of the input shaft 2 is decelerated by the speed reduction planetary gear 6 and the sun gear of the single planetary gear 5 This is transmitted to Sr (seventh element).

  The speed reduction planetary gear 6 includes a sun gear Sa, a ring gear Ra, and a carrier Ca that supports the pinion Pa meshing with the sun gear Sa and the ring gear Ra so as to be capable of rotating and revolving. The sun gear Sa is a fixed element that is fixed to the transmission case 1, the ring gear Ra is an input element that is connected to the input shaft 2, and the carrier Ca that is an output element is connected to the sun gear Sr of the single planetary gear 5 via the third clutch C3. It is connected. Other configurations are the same as those of the second embodiment.

  In the speed diagram of the speed reduction planetary gear 6 shown in the upper part of FIG. 15, the carrier Ca serving as an output element is located between the sun gear Sa and the ring gear Ra. The gear ratio of the planetary gear 6 for deceleration is m, and the ratio between the distance between the sun gear Sa and the carrier Ca and the distance between the carrier Ca and the ring gear Ra is set to m: 1. Then, the output speed (speed of rotation of the carrier Ca) N0 of the deceleration planetary gear 6 is m / (m + 1).

  In the tenth embodiment, when the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotation speed at the vertical line Y3 is N1 (= −1 / i), and the rotation at the vertical line Y5. The speed becomes N0, and the rotation speed on the vertical line Y4 becomes “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 speeds of all the rotating elements of the compound planetary gear 4 become “0”, so the rotational speed at the vertical line Y3 is “0”. ”, The rotational speed at the vertical line Y5 is N0, and the rotational speed at the vertical line Y4 is“ 2nd ”. That is, the second gear is established.

  When the third clutch C3, the fourth clutch C4, 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 N0, and the vertical line Y4 The rotation speed is “3rd”. That is, the third 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 N0, and the vertical line Y4 The rotation speed is “4th”. That is, the fourth gear is established.

  When the first clutch C1, the third clutch C3, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y1 is “1”, the rotational speed at the vertical line Y5 is N0, and the vertical line Y4 The rotation speed is “5th”. That is, the fifth gear is established.

  When the second clutch C2, the third clutch C3, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y2 is “1”, the rotational speed at the vertical line Y5 is N0, and the vertical line Y4 The rotation speed is “6th”. That is, the sixth gear is established.

  When the first clutch C1, the second clutch C2, and the third clutch C3 are engaged, the rotational speed at the vertical line Y3 is “1”, the rotational speed at the vertical line Y5 is N0, and the vertical line Y4 The rotation speed is “7th”. That is, the seventh gear is established.

  When the first clutch C1, the second clutch C2, and the fourth clutch C4 are engaged, the rotational speed at the vertical line Y1 and the rotational speed at the vertical line Y2 are both "1", and the vertical line Y4 The rotational speed is also “8th” which is “1”. That is, the eighth gear is established.

  When the second clutch C2, the third clutch C3 and the first brake B1 are engaged, the rotational speed at the vertical line Y3 is N2 (= 1 + 1 / i), the rotational speed at the vertical line Y5 is N0, The rotation speed at the line Y4 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 Y1 is “0”, the rotational speed at the vertical line Y3 is N2, and the vertical line Y4 The rotation speed 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 Y1 is “1”, the rotational speed at the vertical line Y3 is N1, and the vertical line Y4 The rotation speed becomes negative “Rev”. That is, the reverse gear is established.

  FIG. 14B 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. 14B, the gear ratio i of the first planetary gear 41 of the double planetary gear 4 is 3.0, the gear ratio j of the second planetary gear 42 is 2.0, and the gear ratio k of the single planetary gear 5 is 2.0. The gear ratios of the respective speeds when the gear ratio m of the speed reduction planetary gear 6 is 3.5 are also shown. According to this, the common ratio becomes appropriate and the total range becomes appropriate.

  Also in the tenth embodiment, three of the six engagement elements are engaged at each shift speed, so the number of engagement elements released at each shift speed is three. Become. 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.

  In the tenth embodiment, the rotation of the input shaft 2 is decelerated by the speed reduction planetary gear 6 and transmitted to the sun gear Sr (seventh element) of the single planetary gear 5 and the state in which this transmission is released can be switched. As the third engagement element, the third clutch C3 that connects the output element of the speed reduction planetary gear 6 and the sun gear Sr of the single planetary gear 5 is used. However, as in the eleventh embodiment shown in FIG. 16, the speed reduction planetary gear 6 is used. It is also possible to use a third brake B3 that can be switched between a state in which the fixing element is fixed to the transmission case 1 and a state in which the fixing is released as the third engagement element. Here, in the eleventh embodiment, the fixed element of the speed reduction planetary gear 6 is the sun gear Sr. However, even when the speed reduction planetary gear 6 is of a double pinion type and the carrier is a fixed element, the third clutch C3 is used. Can be replaced with the third brake B3.

  In the fifth to eleventh embodiments, a forward 10-speed shift is possible. However, an 8-speed or 9-speed shift may be omitted and a forward 9-speed shift may be performed.

(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 double planetary gear and the single planetary gear of the first embodiment. The skeleton figure of 2nd Embodiment of this invention transmission. The speed diagram of the compound planetary gear and single planetary gear of 2nd Embodiment. The skeleton figure of 3rd Embodiment of this invention transmission. The speed diagram of the compound planetary gear and single planetary gear of 3rd Embodiment. The skeleton figure of 4th Embodiment of this invention transmission. (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 planetary gear for deceleration of a 5th embodiment, a double type planetary gear, and a single type planetary gear. The skeleton figure of 6th Embodiment of this invention transmission. The skeleton figure of 7th Embodiment of this invention transmission. The skeleton figure of 8th Embodiment of this invention transmission. The skeleton figure of 9th Embodiment of this invention transmission. (A) Skeleton diagram of the tenth 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 speed reduction planetary gear of 10th Embodiment, a double type planetary gear, and a single type planetary gear. The skeleton figure of 11th 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 ... Double planetary gear, Sf ... Sun gear of double planetary gear (1st element) , Cf, Sm... First connection body (second element) of double planetary gear, Rf, Cm... Second connection body (third element) of double planetary gear, Rm... Ring gear (fourth element) of double planetary gear, 5. Planetary gear, Rr ... Ring gear of single planetary gear (fifth element in the first embodiment), Cr ... Carrier of single planetary gear (sixth element in the first embodiment), Sr ... Sun gear of single planetary gear (seventh in the first embodiment) Element), 6 ... planetary gear for reduction, C1 ... first clutch (first engagement element), C2 ... second clutch (second engagement element), 3 ... 3rd clutch (3rd engagement element), C4 ... 4th clutch (4th engagement element), B1 ... 1st brake (5th engagement element), B2 ... 2nd brake (6th engagement element) ), B3... Third brake (first engagement element).

Claims (3)

An automatic transmission that shifts the rotation of the input member to a plurality of stages via an input-side planetary gear and an output-side single planetary gear arranged in the transmission case, and transmits them to the output member.
The compound planetary gear 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 fourth element. The three elements consisting of the sun gear, ring gear and carrier of the single planetary gear are arranged in the order corresponding to the gear ratio in the velocity diagram as the fifth element, the sixth element and the seventh element, respectively. 5 elements are connected and the 6th element is connected to the output member,
A first engagement element switchable between a state in which the rotation of the input member is transmitted to the first element and a state in which the transmission is interrupted;
A second engagement element switchable between a state in which the rotation of the input member is transmitted to the second element and a state in which the transmission is interrupted;
A third engagement element switchable between a state in which the rotation of the input member is transmitted to the seventh element and a state in which this transmission is interrupted;
A fourth engagement element switchable between a state in which the fourth element and the sixth element are connected and a state in which the connection is broken;
A fifth engagement element switchable between a state in which the first 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 second element is fixed to the transmission case and a state in which the fixing is released.   2. The automatic transmission according to claim 1, further comprising a planetary gear for deceleration, wherein rotation of the input member is decelerated by the planetary gear for deceleration and transmitted to the first element when the first engagement element is engaged. An automatic transmission characterized in that.   2. The automatic transmission according to claim 1, further comprising a reduction planetary gear, wherein the rotation of the input member is decelerated by the reduction planetary gear and transmitted to the seventh element when the third engagement element is engaged. An automatic transmission characterized in that.

Images