JP2010169108A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission which includes a combined planetary gear having five rotary elements without increasing the axial length. <P>SOLUTION: The automatic transmission includes input planetary gears 41, 42, and the shifting combined planetary gear 5. The combined planetary gear 5 consists of double pinion type first and third planetary gears 6, 8, and a single pinion type second planetary gear 7. A pinion Pb' engaging with a ring gear Rb of the first planetary gear 6, a pinion Pc of the second planetary gear 7, and a pinion Pd engaging with a sun gear Sd of the third planetary gear 8 are integrated with one another, a ring gear Rc of the second planetary gear 7 is integrated with the ring gear Rb of the first planetary gear 6, and a sun gear Sc of the second planetary gear 7 is integrated with the sun gear Sd of the third planetary gear 8. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

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

  There is known an automatic transmission in which the rotation of an input shaft is shifted to a plurality of stages and transmitted to an output member via an input planetary gear arranged concentrically with the input shaft and a double planetary gear for shifting (for example, patent document) 1).

  In Patent Document 1, the first planetary gear for input is constituted by a single pinion type, and the double planetary gear is constituted by a single pinion type second planetary gear and a double pinion type third planetary gear. In the double planetary gear, the ring gears of the second planetary gear and the third planetary gear are constituted by the same member, and the pinion supported by the carrier of the second planetary is used for one of the pair of pinions of the third planetary gear, and the carrier of the second planetary gear and the second planetary gear A Ravigneaux type planetary gear is constituted by connecting the carrier of the three planetary gears and the second and third planetary gears. The compound planetary gear includes a first rotating element composed of a sun gear of the second planetary gear, a second rotating element composed of a carrier of the second and third planetary gears, and a third planetary gear ring gear shared with the ring gear of the third planetary gear. A rotating element and a fourth rotating element comprising a sun gear of a third 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 connected to the output member.

  Further, as the engagement element, a first clutch that can be switched between a state in which the rotation of the input member is decelerated and transmitted to the fourth rotation element via the first planetary gear and a state in which the transmission is cut off, and a second rotation element A second clutch that can be switched between a state in which the input member is connected and a state in which the connection is cut off, a state in which the rotation of the input member is decelerated and transmitted to the first rotating element via the first planetary gear, and the transmission is cut off. A third clutch that can be switched between a state, a fourth clutch that can be switched between a state in which the third rotating element and the input member are connected, and a state in which the connection is broken, and a first rotating element that is fixed to the transmission case. A first brake which can be switched between a state and a state where the fixing is released, and a second brake which can be switched between a state where the second rotating element is fixed to the transmission case and a state where the fixing is released. .

  According to the above configuration, the first gear is established by engaging the first clutch and the second brake, the second gear is established by engaging the first clutch and the first brake, The third speed is established by engaging the first and third clutches, the fourth speed is established by engaging the first and second clutches, and the second 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 second clutch and the first brake. Is established.

Japanese Patent Laying-Open No. 2005-54824 (FIG. 1-3)

  The compound planetary gear of the conventional example is composed of two planetary gears and includes four rotating elements. However, the compound planetary gear is composed of three planetary gears and includes five rotating elements. It is conceivable to improve the degree of freedom in setting the ratio of the gear ratio between the two. However, if one planetary gear is added, the axial length of the automatic transmission is increased by that amount, and the mountability on the vehicle is impaired.

  In view of the above, an object of the present invention is to provide an automatic transmission including a double planetary gear having five rotating elements without increasing the axial length.

  To achieve the above object, according to a first aspect of the present invention, there is provided an output member in which rotation of an input shaft is shifted in a plurality of stages via an input planetary gear arranged concentrically with the input shaft and a multiple planetary gear for shifting. The double planetary gear includes a first planetary gear, a second planetary gear, and a third planetary gear, and the first and third planetary gears mesh with each other and one of the sun gear and the ring gear. Each of the second planetary gears includes a sun gear, a ring gear, and a pinion that meshes with the sun gear and the ring gear. A pinion configured to freely support the carrier and mesh with the ring gear of the first planetary gear; The pinion of the second planetary gear and the pinion meshing with the sun gear of the third planetary gear are integrated, the ring gear of the second planetary gear is integrated with the ring gear of the first planetary gear, and the sun gear of the second planetary gear is integrated with the sun gear of the third planetary gear It is characterized by being.

  According to the first aspect of the present invention, all the elements of the sun gear, the ring gear and the carrier of the second planetary gear are integrated with the elements of the first or third planetary gear, and the double planetary gear is substantially the first and third. The two planetary gears can be used. Therefore, a double planetary gear having five rotating elements can be configured without increasing the shaft length, and the common ratio of the automatic transmission (the ratio of the gear ratio between the respective gears can be reduced without impairing the mountability on the vehicle. Ratio) can be improved.

  As a first specific example of the automatic transmission according to the first aspect of the present invention, for example, fourth and fifth planetary gears for input are provided, and the fourth and fifth planetary gears are connected to the input shaft. The first to third planetary gears of the double planetary gear, each having an input element, a fixed element fixed to the transmission case, and an output element, are configured to shift the rotation of the input shaft and output from the output element. The sun gear, ring gear, and carrier elements of the above constitute five rotating elements arranged at intervals corresponding to the gear ratio in the velocity diagram, and these rotating elements are arranged in the order of arrangement in the velocity diagram, respectively, as the first rotating element and the second rotating element. As the element, the third rotating element, the fourth rotating element, and the fifth rotating element, the second rotating element is the output element of the fifth planetary gear, the fourth rotating element is the output element of the fourth planetary gear, and the third rotating element is the output unit A first engaging element that can be switched between a state in which the first rotating element is connected to the input shaft and a state in which the connection is cut off, and a state in which the fifth rotating element is connected to the input shaft. A second engagement element that can be switched to a state in which the connection is broken, a third engagement element that can be switched to a state in which the fourth rotation element is fixed to the transmission case, and a state in which the fixation is released, A fourth engaging element that can be switched between a state in which the fixing element of the four planetary gear is fixed to the transmission case and a state in which the fixing is released; a state in which the fixing element of the fifth planetary gear is fixed to the transmission case; It can comprise so that the 5th engagement element switchable to the state to cancel | release will be provided.

  According to such a configuration, although two planetary gears are used for input, substantially four planetary gears and five engaging elements are used, as will be apparent from the description of the embodiment described later, seven forward speeds. Can be changed.

  In the first specific example of the present invention, the fourth planetary gear for input is output from the output element by accelerating the rotation of the input shaft input to the input element, and the fifth planetary gear for input is If the rotation of the input shaft input to the input element is decelerated and output from the output element, the degree of freedom in setting the common ratio (ratio ratio between each gear) can be further improved. Both the ratio of the first gear / the ratio of the seventh gear) and the common ratio can be set to suitable values.

  As a second specific example of the automatic transmission according to the first aspect of the present invention, for example, a fourth planetary gear for input is provided, and the fourth planetary gear is fixed to the transmission case and an input element coupled to the input shaft. Each of the sun gear, ring gear, and carrier elements of the first to third planetary gears of the double planetary gear, each having a fixed element and an output element that are configured to shift the rotation of the input shaft and output from the output element. Comprises five 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 rotating element, the second rotating element, the third rotating element, and the fourth rotating element. As the rotating element and the fifth rotating element, the third rotating element is connected to the output element of the fourth planetary gear, the fourth rotating element is connected to the output member, and the first rotating element is connected to the input shaft as the engaging element. A first engagement element that can be switched between a state and a state in which the connection is cut off, a second engagement element that is switchable between a state in which the fifth rotation element is connected to the input shaft and a state in which the connection is cut off, and a third A third engaging element that can be switched between a state in which the rotating element is fixed to the transmission case and a state in which the fixing is released, a state in which the fixing element of the fourth planetary gear is fixed to the transmission case, and a state in which the fixing is released A fourth engaging element that can be switched between, a fifth engaging element that can be switched between a state in which the first rotating element is fixed to the transmission case and a state in which the fixing is released, and a second rotating element that is connected to the input shaft And a sixth engaging element that is switchable between a state of being connected to the state of being disconnected and a state of being disconnected.

  According to such a configuration, as is apparent from the description of the embodiment described later, it is possible to perform a forward eight-speed shift by using a total of three planetary gears and six engaging elements in total including the input planetary gears. .

  In the second specific example of the present invention, if the fourth planetary gear for input increases the rotation of the input shaft input to the input element and outputs it from the output element, a good reduction ratio can be obtained. be able to.

  According to a second aspect of the present invention, there is provided an automatic transmission in which a rotation of an input shaft is shifted to a plurality of stages through a planetary gear for input arranged concentrically with the input shaft and transmitted to an output member through a multiple planetary gear for shifting. The compound planetary gear includes a first planetary gear, a second planetary gear, and a third planetary gear, and the first and second planetary gears are capable of freely rotating and revolving a sun gear, a ring gear, and a pinion that meshes with the sun gear and the ring gear. The third planetary gear includes a sun gear, a ring gear, and a carrier that rotatably and reciprocally supports a pair of pinions that mesh with each other and one meshes with the sun gear and the other meshes with the ring gear. The first planetary gear pinion and the second planetary gear pinion and the third planetary are configured. Any one of the pair of pinions is integrated, the sun gear of the second planetary gear is integrated with the sun gear of the third planetary gear, the ring gear of the second planetary gear is integrated with the ring gear of the first planetary gear, The gear ratio of the first planetary gear and the gear ratio of the second planetary gear are different from each other.

  According to the second aspect of the present invention, as in the first aspect, all the elements of the sun gear, the ring gear and the carrier of the second planetary gear are integrated with the elements of the first or third planetary gear, and the double planetary gear is The first and third planetary gears can be substantially constituted. Therefore, a double planetary gear having five rotating elements can be configured without increasing the shaft length, and the common ratio of the automatic transmission (the ratio of the gear ratio between the respective gears can be reduced without impairing the mountability on the vehicle. Ratio) can be improved.

  Here, in order to make the gear ratio of the first planetary gear different from the gear ratio of the second planetary gear, it is necessary to make the number of teeth of both sun gears different.

  Therefore, the present invention is configured such that the pinion of the first planetary gear is configured with a stepped pinion having a large diameter portion and a small diameter portion having different numbers of teeth, and the sun gear of the first planetary gear is configured with a large diameter portion and a small diameter portion of the stepped pinion. And the ring gear of the first planetary gear is meshed with either the large diameter portion or the small diameter portion of the stepped pinion, and the sun gear of the third planetary gear is meshed with the large diameter portion or the small diameter portion of the stepped pinion. The ring gear of the third planetary gear or the pinion meshing with the ring gear is meshed with either the large diameter portion or the small diameter portion of the stepped pinion, and the pinion of the second planetary gear is It is composed of either the large diameter part or the small diameter part of the attached pinion. Thereby, the difference in the number of teeth of the sun gear of the first and second planetary gears can be set large, and the degree of freedom in setting the common ratio can be greatly improved.

  Specific examples of the automatic transmission according to the second aspect of the present invention include, for example, input fourth and fifth planetary gears, and the fourth and fifth planetary gears are input elements connected to the input shaft. And a fixed element fixed to the transmission case, and an output element, and configured to shift the rotation of the input shaft and output from the output element, and the sun gears of the first to third planetary gears of the double planetary gear , Each element of the ring gear and the carrier constitutes five rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the order in the speed diagram, respectively, the first rotating element, the second rotating element, As the third rotating element, the fourth rotating element, and the fifth rotating element, the second rotating element is the output element of the fourth planetary gear, the fifth rotating element is the output element of the fifth planetary gear, and the third rotating element is the output member. A first engagement element that is connected and can be switched between a state in which the first rotation element is connected to the input shaft and a state in which the connection is broken, and a state in which the fourth rotation element is connected to the input shaft. A second engagement element that can be switched to a state in which the connection is broken, a third engagement element that can be switched to a state in which the fourth rotation element is fixed to the transmission case, and a state in which the fixation is released, and a fourth A fourth engaging element that can be switched between a state in which the planetary gear fixing element is fixed to the transmission case and a state in which this fixing is released, and a state in which the fixing element of the fifth planetary gear is fixed to the transmission case and the fixing are released. A fifth engagement element that is switchable to a state of being engaged.

  According to such a configuration, although two planetary gears are used for input, substantially four planetary gears and five engaging elements are used, as will be apparent from the description of the embodiment described later, seven forward speeds. Can be changed.

  In the specific example of the second aspect of the present invention, the fourth and fifth planetary gears for input are output from the output element by decelerating the rotation of the input shaft input to the input element. If the gear ratio of the planetary gear and the gear ratio of the fifth planetary gear are different from each other, the degree of freedom in setting the common ratio (ratio ratio between the respective gears) can be further improved. Both the 7th gear ratio) and the common ratio can be set to suitable values.

(A) is a skeleton diagram of the first embodiment of the automatic transmission according to the present invention, and (b) is a diagram collectively showing the relationship between each shift stage and the engagement state of each engagement element of the first embodiment. The speed diagram of the 1st-5th planetary gear of 1st Embodiment. The skeleton figure of 2nd Embodiment of the automatic transmission of this invention. (A) is a skeleton figure of 3rd Embodiment of the automatic transmission of this invention, (b) is a figure which shows collectively the relationship between each gear stage of 3rd Embodiment, and the engagement state of each engagement element. The speed diagram of the 1st-4th planetary gear of 3rd Embodiment. The skeleton figure of 4th Embodiment of the automatic transmission of this invention. (A) is a skeleton figure of 5th Embodiment of the automatic transmission of this invention, (b) is a figure which shows collectively the relationship between each gear stage of 5th Embodiment, and the engagement state of each engagement element. The speed diagram of the 1st-5th planetary gear of 5th Embodiment.

  Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. The automatic transmission according to the first embodiment includes an input shaft 2 that is rotatably supported in a transmission case 1 and connected to a power source such as an engine (not shown), and an output 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, the fourth and fifth planetary gears 41 and 42 for input and the double planetary gear 5 for shifting are arranged around the input shaft 2.

  The compound planetary gear 5 is composed of first to third planetary gears 6, 7, and 8. The first planetary gear 6 includes a sun gear Sb, a ring gear Rb, and a carrier Cb that supports a pair of pinions Pb and Pb ′ that mesh with each other and one meshes with the sun gear Sb and the other meshes with the ring gear Rb. Consists of a double pinion type planetary gear. The second planetary gear 7 is composed of a single pinion type planetary gear including a sun gear Sc, a ring gear Rc, and a carrier Cc that supports the sun gear Sb and the pinion Pc meshing with the ring gear Rc so as to rotate and revolve. Similar to the first planetary gear 6, the third planetary gear 8 is capable of rotating and revolving a pair of pinions Pd and Pd ′ meshing with the sun gear Sd and the ring gear Rd and one meshing with the sun gear Sd and the other meshing with the ring gear Rd. And a double-pinion type planetary gear comprising a carrier Cd supported on the surface.

  The sun gear Sc of the second planetary gear 7 is integrated with the sun gear Sd of the third planetary gear 8, the ring gear Rc of the second planetary gear 7 is integrated with the ring gear Rb of the first planetary gear 6, and the pinion Pc of the second planetary gear 7 and The pinion Pd that meshes with the sun gear Sd of the third planetary gear 8 is integrated with the pinion Pb ′ that meshes with the ring gear Rb of the first planetary gear 6.

  Therefore, the carrier Cc of the second planetary gear 7 is also integrated with the portion of the carrier Cb that supports the pinion Pb ′ of the first planetary gear 6. That is, since all the constituent elements of the second planetary gear 7 are integrated with the constituent elements of the first planetary gear 6 or the third planetary gear 8, the double planetary gear 5 is substantially composed of the first and third planetary gears 6,6. 8 is configured.

  Further, the portion of the third planetary gear 8 that supports the pinion Pd of the carrier Cd is integrated with the portion of the first planetary gear 6 that supports the pinion Pb ′ of the carrier Cb, and thus the carrier Cb of the first planetary gear 6 is supported. Are connected to the carrier Cd of the third planetary gear 8.

  The double planetary gear 5 includes five rotating elements represented by vertical lines, as shown in the lower speed diagram of FIG. Assuming that each rotation element shown in FIG. 2 is, in order from the left, the first rotation element Y1, the second rotation element Y2, the third rotation element Y3, the fourth rotation element Y4, and the fifth rotation element Y5, the first rotation element Y1 is the sun gear Sb of the first planetary gear 6, the second rotating element Y2 is the ring gear Rb of the first planetary gear 6 and the ring gear Rc of the second planetary gear 7, and the third rotating element Y3 is the carrier Cb of each of the first to third planetary gears. Cc, Cd, the fourth rotation element Y4 is constituted by the ring gear Rd of the third planetary gear 8, and the fifth rotation element Y5 is constituted by the sun gear Sc of the second planetary gear 7 and the sun gear Sd of the third planetary gear. In the velocity diagram of the compound planetary gear 5, the lower horizontal line indicates that the rotational speed is “0”, and the upper horizontal line indicates that the rotational speed is “1”, which is the same as “1”. ".

  When the gear ratio of the first planetary gear 6 (the number of teeth of the ring gear / the number of teeth of the sun gear) is i, the gear ratio of the second planetary gear 7 is j, and the gear ratio of the third planetary gear 8 is k, the first to fifth each The interval between the rotating elements is a ratio of i−1: 1: k / j: j−k / j.

  The first rotation element Y1 is freely connectable to the input shaft 2 by a first clutch C1 that is a first engagement element. Further, the fifth rotation element Y5 is freely connectable to the input shaft 2 by the second clutch C2 as the second engagement element. The fourth engagement element Y4 can be fixed to the transmission case 1 by the first brake B1 as the third engagement element. The third rotating element Y3 is connected to the output gear 3.

  The fourth and fifth planetary gears 41 and 42 for input support the sun gears Sa1 and Sa2, the ring gears Ra1 and Ra2, and the pinions Pa1 and Pa2 meshing with the sun gears Sa1 and Sa2 and the ring gears Ra1 and Ra2 so as to freely rotate and revolve. Single-pinion type planetary gears composed of carriers Ca1 and Ca2.

  The carrier Ca1 of the fourth planetary gear 41 is connected to the input shaft 2, and the sun gear Sa1 can be fixed to the transmission case 1 by a second brake B2 that is a fourth engagement element. Therefore, the input element of the fourth planetary gear 41 is the carrier Ca1, the fixed element is the sun gear Sa1, and the output element is the ring gear Ra1.

  When the gear ratio of the fourth planetary gear 41 (the number of teeth of the ring gear / the number of teeth of the sun gear) is m, when the second brake B2 is engaged, the rotational speed of the carrier Ca1 is “1” and the rotational speed of the sun gear Sa1 is The rotational speed N1 of the ring gear Ra1 as an output element is increased to (m + 1) / m. The ring gear Ra1 as an output element of the fourth planetary 41 is connected to the fourth rotation element Y4 of the double planetary gear 5.

  The ring gear Ra2 of the fifth planetary gear 42 is connected to the input shaft 2, and the sun gear Sa2 can be fixed to the transmission case 1 by a third brake B3 that is a fifth engagement element. Therefore, the input element of the fifth planetary gear 42 is the ring gear Ra2, the fixed element is the sun gear Sa2, and the output element is the carrier Ca2.

  When the gear ratio of the fifth planetary gear 42 is n, when the third brake B3 is engaged, the rotational speed of the ring gear Ra2 is "1", the rotational speed of the sun gear Sa2 is "0", and the carrier Ca2 that is an output element The rotational speed N2 is decelerated to n / (n + 1). A carrier Ca <b> 2 that is an output element of the fifth planetary 42 is coupled to the second rotation element Y <b> 2 of the double planetary gear 5.

  When the first clutch C1 and the first brake B1 are engaged, the rotation speed of the first rotation element Y1 is “1”, the rotation speed of the fourth rotation element Y4 is “0”, and the first gear connected to the output gear 3 is connected. The third rotation element Y3 rotates at “1st”, and the first gear is established.

  When the first brake B1 and the third brake B3 are engaged, the rotation speed of the fourth rotation element Y4 is “0”, the rotation speed of the second rotation element Y2 is N2, and the third rotation element Y3 is “2nd”. And the second gear is established.

  When the first clutch C1 and the third brake B3 are engaged, the rotation speed of the first rotation element Y1 is “1”, the rotation speed of the second rotation element Y2 is N2, and the third rotation element Y3 is “3rd”. To establish the third gear.

  When the second clutch C2 and the third brake B3 are engaged, the rotation speed of the fifth rotation element Y5 is “1”, the rotation speed of the second rotation element Y2 is N2, and the third rotation element Y3 is “4th”. To establish the fourth gear.

  When the first clutch C1 and the second clutch C2 are engaged, the rotating elements of the compound planetary gear 5 are not allowed to rotate relative to each other, the rotation speeds of all the rotating elements are “1”, and the third rotating element Y3 is Rotating at “5th”, which is “1”, establishes the fifth gear.

  When the first clutch C1 and the second brake B2 are engaged, the rotation speed of the first rotation element Y1 is “1”, the rotation speed of the fourth rotation element Y4 is N1, and the third rotation element Y3 is “6th”. And the 6th gear is established.

  When the second clutch C2 and the second brake B2 are engaged, the rotation speed of the fifth rotation element Y5 is “1”, the rotation speed of the fourth rotation element Y4 is N1, and the third rotation element Y3 is “7th”. To establish the seventh gear.

  When the second clutch C2 and the first brake B1 are engaged, the rotation speed of the fifth rotation element Y5 is “1”, the rotation speed of the fourth rotation element Y4 is “0”, and the third rotation element Y3 is reversed. A reverse gear is established by rotating at “Rev” of (reverse direction rotation).

  FIG. 1 (b) collectively shows the engagement state of each engagement element at each shift stage described above, and “◯” represents engagement. 1B shows that the gear ratio i of the first planetary gear 6 is 3.0, the gear ratio j of the second planetary gear 7 is 2.6, the gear ratio m of the fourth planetary gear 41 is 3.5, When the gear ratio n of the planetary gear 42 is 3.0, and the value q obtained by dividing the number of teeth of the ring gear Rd of the third planetary gear 8 by the number of teeth of the sun gear Sb of the first planetary gear 6 is 3.2 (in this case, the third Also shown is the gear ratio (rotational speed of the input shaft 2 / rotational speed of the output gear 3) of each gear position at a gear ratio k of the planetary gear 8 of about 2.773. According to this, the public ratio (ratio of gear ratios between the respective gears) becomes appropriate, and ratio orange (ratio of the gear ratio of the first gear to the gear ratio of the seventh gear (the ratio of the first gear of FIG. 1B) Appropriate ratio))) is also appropriate.

  According to the automatic transmission of the first embodiment, all the elements of the sun gear Sc, the ring gear Rc, and the carrier Cc of the second planetary gear 7 are integrated with the elements of the first planetary gear 6 or the third planetary gear 8, and the double planetary gear 5 Is substantially constituted by the first and third planetary gears 6 and 8. Therefore, the compound planetary gear 5 having the five rotary elements Y1 to Y5 can be configured without increasing the shaft length of the automatic transmission, and the common ratio of the automatic transmission can be reduced without impairing the mounting property on the vehicle. The degree of freedom in setting (the ratio of gear ratios between gears) can be improved.

  Further, as the planetary gear for input, the fourth planetary gear 41 and the fifth planetary gear 42 are used. The fourth planetary gear 41 is output from the ring gear Ra1 as an output element by increasing the rotation speed of the input shaft 2, and the fifth planetary gear. Since the rotation of the input shaft 42 is decelerated and output from the carrier Ca2, which is an output element, the degree of freedom in setting the common ratio (ratio ratio between each gear) is further improved.

  The double planetary gear 5 is in a state of being reversed left and right as in the second embodiment shown in FIG. 3, and the first rotation element Y1 is moved to the sun gear Sc of the second planetary gear 7, the sun gear Sd of the third planetary gear 8, and the second rotation. The element Y2 is the ring gear Rd of the third planetary gear 8, the third rotation element Y3 is the carriers Cb, Cc, Cd of the first to third planetary gears, the fourth rotation element Y4 is the ring gear Rb of the first planetary gear 6, and the second planetary gear. The ring gear Rc and the fifth rotation element Y5 may be constituted by the sun gear Sb of the first planetary gear 6. In this case, the other configurations are the same as those in the first embodiment, the respective shift stages are established in the same manner, and the same effects as those in the first embodiment can be obtained.

  Next, with reference to FIG.4 and FIG.5, the automatic transmission of 3rd Embodiment is demonstrated. In the automatic transmission according to the third embodiment, instead of the fifth planetary gear 42 according to the first embodiment, a second rotating element Y2 configured by a ring gear Rb of the first planetary gear 6 and a ring gear Rc of the second planetary gear 7 is input. A third clutch C3, which is a sixth engagement element that can be connected to the shaft 2, is provided, and a ring gear Ra1, which is an output element of the fourth planetary gear 41, is connected to the carriers Cb, Cc of the first to third planetary gears 6, 7, 8, The output gear 3 is connected to the fourth rotating element Y4 configured by the ring gear Rd of the third planetary gear 8 and the third rotating element Y3 is connected to the transmission case 1. A first rotating element Y1 composed of a first brake B1 as a third engaging element that can be fixed and a sun gear Sb of the first planetary gear 6 can be fixed to the transmission case 1 as a fifth. The third brake B3 serving coupling elements, allowing the forward rotation of the third rotating element Y3 (rotation in the forward direction), and a one-way clutch F1 to prevent reverse rotation. Other configurations are the same as those of the first embodiment.

  In the third embodiment, when the second clutch C2 and the first brake B1 are engaged, the rotation speed of the fifth rotation element Y5 is “1”, the rotation speed of the third rotation element Y3 is “0”, The rotation speed of the fourth rotation element Y4 connected to the output gear 3 becomes “1st” shown in FIG. 5, and the first gear is established. The third rotation element Y3 is provided with a one-way clutch F1 that prevents reverse rotation (reverse rotation), so that when the vehicle is accelerating, the third rotation is performed by the one-way clutch F1. The rotational speed of the element Y3 is “0”. For this reason, when the vehicle is accelerating, the first brake B1 does not necessarily have to be engaged.

  When the second clutch C2 and the third brake B3 are engaged, the rotation speed of the fifth rotation element Y5 becomes “1”, the rotation speed of the first rotation element Y1 becomes “0”, and the rotation of the fourth rotation element Y4 The speed becomes “2nd” shown in FIG. 5 and the second gear is established.

  When the first clutch C1 and the second clutch C2 are engaged, the compound planetary gear 5 is in a locked state where the respective elements cannot be rotated relative to each other, and the rotation speed of the fourth rotation element Y4 is “3rd”, which is “1”. Thus, the third gear is established. At this time, if the third clutch C3 is also engaged, the occurrence of friction loss in the third clutch C3 can be reliably prevented.

  When the second clutch C2 and the second brake B2 are engaged, the rotation speed of the fifth rotation element Y5 is “1”, the rotation speed of the third rotation element Y3 is N1, and the rotation speed of the fourth rotation element Y4 is “4th” shown in FIG. 5 is established, and the fourth gear is established.

  When the first clutch C1 and the second brake B2 are engaged, the rotation speed of the first rotation element Y1 is “1”, the rotation speed of the third rotation element Y3 is N1, and the rotation speed of the fourth rotation element Y4 is “5th” shown in FIG. 5 is established, and the fifth gear is established.

  When the third clutch C3 and the second brake B2 are engaged, the rotation speed of the second rotation element Y2 is “1”, the rotation speed of the third rotation element Y3 is N1, and the rotation speed of the fourth rotation element Y4 is “6th” shown in FIG. 5 is established, and the sixth gear is established.

  When the second brake B2 and the third brake B3 are engaged, the rotation speed of the third rotation element Y3 is N1, the rotation speed of the first rotation element Y1 is “0”, and the rotation speed of the fourth rotation element Y4 is “7th” shown in FIG. 5 is established, and the seventh gear is established.

  When the third clutch C3 and the third brake B3 are engaged, the rotation speed of the second rotation element Y2 becomes “1”, the rotation speed of the first rotation element Y1 becomes “0”, and the rotation of the fourth rotation element Y4 The speed becomes “8th” shown in FIG. 5, and the eighth gear is established.

  When the first clutch C1 and the first brake B1 are engaged, the rotation speed of the first rotation element Y1 becomes “1”, the rotation speed of the third rotation element Y3 becomes “0”, and the rotation of the fourth rotation element Y4 As shown in FIG. 5, the reverse speed (reverse rotation) “Rev1” is established, and the first reverse speed is established.

  When the third clutch C3 and the first brake B1 are engaged, the rotation speed of the second rotation element Y2 becomes “1”, the rotation speed of the third rotation element Y3 becomes “0”, and the rotation of the fourth rotation element Y4 As shown in FIG. 5, the reverse speed (reverse direction rotation) “Rev2” is established, and the second reverse speed is established.

  FIG. 4B collectively shows the engagement state of each engagement element at each shift stage described above, and “◯” indicates engagement. 4B, the gear ratio i of the first planetary gear 6 is 3.0, the gear ratio j of the second planetary gear 7 is 2.4, the gear ratio k of the third planetary gear 8 is 2.4, Also shown is the gear ratio (rotational speed of the input shaft 2 / rotational speed of the output gear 3) of each gear when the gear ratio m of the planetary gear 42 is 3.0. According to this, the public ratio (ratio of the gear ratio between the respective gears) becomes appropriate, and the ratio orange (ratio of the gear ratio of the first gear to the gear ratio of the eighth gear (the gear ratio of the first gear in FIG. 4 (b)). Appropriate ratio))) is also appropriate.

  According to the automatic transmission of the third embodiment, all the elements of the sun gear Sc, the ring gear Rc, and the carrier Cc of the second planetary gear 7 are integrated with the elements of the first planetary gear 6 or the third planetary gear 8, and the double planetary gear 5 Is substantially constituted by the first and third planetary gears 6 and 8. Therefore, the compound planetary gear 5 having the five rotary elements Y1 to Y5 can be configured without increasing the shaft length of the automatic transmission, and the common ratio of the automatic transmission can be reduced without impairing the mounting property on the vehicle. The degree of freedom in setting (the ratio of gear ratios between gears) can be improved.

  Note that the compound planetary gear 5 of the third embodiment is in a state of being reversed left and right as in the fourth embodiment shown in FIG. 6, and the first rotating element Y1 is set to the sun gear Sc of the second planetary gear 7 and the sun gear of the third planetary gear 8. Sd, the second rotation element Y2 is the ring gear Rd of the third planetary gear 8, the third rotation element Y3 is the carriers Cb, Cc, Cd of the first to third planetary gears, and the fourth rotation element Y4 is the ring gear of the first planetary gear 6. Rb, the ring gear Rc of the second planetary gear 7 and the fifth rotating element Y5 may be constituted by the sun gear Sb of the first planetary gear 6. In this case, the other configurations are the same as those in the third embodiment, the respective shift stages are established in the same manner, and the same effects as those in the third embodiment can be obtained.

  Next, an automatic transmission according to a fifth embodiment of the present invention will be described with reference to FIGS. In the transmission case 1 of the automatic transmission according to the fifth embodiment, the fourth and fifth planetary gears 41 and 42 for input and the double planetary gear 5 for shifting are positioned around the input shaft 2. And are arranged.

  The compound planetary gear 5 is composed of first to third planetary gears 6, 7, and 8. The first planetary gear 6 is formed of a single pinion type planetary gear including a sun gear Sb, a ring gear Rb, and a carrier Cb that supports the sun gear Sb and the pinion Pb meshing with the ring gear Rb so as to rotate and revolve. The pinion Pb is composed of a stepped pinion composed of a small diameter part Pb1 and a large diameter part Pb2. The sun gear Sb meshes with the small diameter part Pb1 of the pinion Pb, and the ring gear Rb meshes with the large diameter part Pb2. The second planetary gear 7 is composed of a single pinion type planetary gear including a sun gear Sc, a ring gear Rc, and a carrier Cc that supports the sun gear Sc and the pinion Pc meshing with the ring gear Rc so as to freely rotate and revolve. The third planetary gear 8 includes a sun gear Sd, a ring gear Rd, and a carrier Cd that supports a pair of pinions Pd and Pd ′ that mesh with each other and one meshes with the sun gear Sd and the other meshes with the ring gear Rd. Consists of a double pinion type planetary gear. The pinion Pd that meshes with the sun gear Sd is integrated with the pinion Pb of the first planetary gear 6, the sun gear Sd of the third planetary gear 8 meshes with the large-diameter portion Pb2 of the pinion Pd, and the other pinion Pd with the small-diameter portion Pb1. 'Is engaged.

  The sun gear Sc of the second planetary gear 7 is integrated with the sun gear Sd of the third planetary gear 8, the ring gear Rc of the second planetary gear 7 is integrated with the ring gear Rb of the first planetary gear 6, and the pinion Pc of the second planetary gear 7 is The large diameter portion Pb2 of the pinion Pb meshing with the sun gear Sb of the first planetary gear 6 is integrated.

  Accordingly, the carrier Cc of the second planetary gear 7 is also integrated with the carrier Cb of the first planetary gear 6. That is, since all the constituent elements of the second planetary gear 7 are integrated with the constituent elements of the first planetary gear 6 or the third planetary gear 8, the double planetary gear 5 is substantially composed of the first and third planetary gears 6,6. 8 is configured.

  Further, the portion of the third planetary gear 8 that supports the pinion Pd of the carrier Cd is integrated with the carrier Cb of the first planetary gear 6, whereby the carrier Cb of the first planetary gear 6 and the carrier Cd of the third planetary gear 8. And are connected.

  The compound planetary gear 5 includes five rotating elements represented by vertical lines, as shown in the velocity diagram in the lower part of FIG. Assuming that the rotation elements shown in FIG. 8 are, in order from the left, the first rotation element Y1, the second rotation element Y2, the third rotation element Y3, the fourth rotation element Y4, and the fifth rotation element Y5, the first rotation element Y1 is the sun gears Sc and Sd of the second and third planetary gears 7 and 8, the second rotating element Y2 is the sun gear Sb of the first planetary gear 6, the third rotating element Y3 is the ring gear Rd of the third planetary gear 8, and the fourth rotating element. Y4 is constituted by the carriers Cb, Cc, Cd of the first to third planetary gears 6, 7, 8 and the fifth rotating element Y5 is constituted by the ring gear Rb of the first planetary gear 6 and the ring gear Rc of the second planetary gear 7.

  The first rotation element Y1 is freely connectable to the input shaft 2 by a first clutch C1 that is a first engagement element. The fourth rotation element Y4 can be connected to the input shaft 2 by the second clutch C2 as the second engagement element, and can be fixed to the transmission case 1 by the first brake B1 as the third engagement element. Has been. The third rotating element Y3 is connected to the output gear 3.

  The gear ratio of the first planetary gear 6 (product of “number of teeth of the ring gear Rb / number of teeth of the sun gear Sb” and “number of teeth of the large diameter portion Pb2 of the stepped pinion Pb / number of teeth of the small diameter portion Pb1”) is i, The gear ratio of the second planetary gear 7 (the number of teeth of the ring gear Rc / the number of teeth of the sun gear Sc) is j, and the gear ratio of the third planetary gear 8 (the number of teeth of the ring gear Rd / the number of teeth of the sun gear Sd) and the stepped pinion Pb. Product of the number of teeth of the small-diameter portion Pb1 / the number of teeth of the large-diameter portion Pb2) is k), the interval between the rotating elements is divided by ji: ij / k: j / k: 1. It is a good match.

  The fourth and fifth planetary gears 41 and 42 for input support the sun gears Sa1 and Sa2, the ring gears Ra1 and Ra2, and the pinions Pa1 and Pa2 meshing with the sun gears Sa1 and Sa2 and the ring gears Ra1 and Ra2 so that they can rotate and revolve freely. Single-pinion type planetary gears comprising carriers Ca1 and Ca2 to be operated.

  The ring gears Ra1 and Ra2 of the fourth and fifth planetary gears 41 and 42 are respectively connected to the input shaft 2, and the sun gear Sa1 of the fourth planetary gear is fixed to the transmission case 1 by the second brake B2 as a fourth engagement element. The sun gear Sa2 of the fifth planetary gear can be fixed to the transmission case 1 by a third brake B3 as a fifth engagement element. Accordingly, the input elements of the fourth and fifth planetary gears 41 and 42 are ring gears Ra1 and Ra2, the fixed elements are sun gears Sa1 and Sa2, and the output elements are carriers Ca1 and Ca2.

  When the gear ratio of the fourth planetary gear 41 is m and the gear ratio of the fifth planetary gear 42 is n, the gear ratio m and the gear ratio n are set differently, and the first brake B1 or the second brake B2 is When engaged, the rotational speed of the ring gear Ra1 or the ring gear Ra2 is "1", the rotational speed of the sun gear Sa1 or the sun gear Sa2 is "0", and the rotational speeds N1 and N2 of the carrier Ca1 or the carrier Ca2 as output elements are m / Decelerated to (m + 1) or n / (n + 1). The carrier Ca1 as an output element of the fourth planetary gear 41 is connected to the second rotating element Y2 of the double planetary gear 5, and the carrier Ca2 as the output element of the fifth planetary gear 42 is connected to the fifth rotating element Y5 of the double planetary gear 5. ing.

  When the first clutch C1 and the first brake B1 are engaged, the rotation speed of the first rotation element Y1 is “1”, the rotation speed of the fourth rotation element Y4 is “0”, and the first gear connected to the output gear 3 is connected. The third rotation element Y3 rotates at “1st”, and the first gear is established.

  When the first brake B1 and the second brake B2 are engaged, the rotation speed of the fourth rotation element Y4 is “0”, the rotation speed of the second rotation element Y2 is N1, and the third rotation element Y3 is “2nd”. And the second gear is established.

  When the first clutch C1 and the second brake B2 are engaged, the rotation speed of the first rotation element Y1 is “1”, the rotation speed of the second rotation element Y2 is N1, and the third rotation element Y3 is “3rd”. To establish the third gear.

  When the second brake B2 and the third brake B3 are engaged, the rotation speed of the second rotation element Y2 is N1, the rotation speed of the fifth rotation element Y5 is N2, and the third rotation element Y3 rotates at “4th”. Thus, the fourth gear is established.

  When the second clutch C2 and the second brake B2 are engaged, the rotation speed of the fourth rotation element Y4 is “1”, the rotation speed of the second rotation element Y2 is N1, and the third rotation element Y3 is “5th”. And the fifth gear is established.

  When the first clutch C1 and the second clutch C2 are engaged, the first to fifth rotating elements of the compound planetary gear 5 are unable to rotate relative to each other, and the rotation speeds of all the rotating elements are “1”. The third rotation element Y3 rotates at “6th” which is “1”, and the sixth gear is established.

  When the second clutch C2 and the third brake B3 are engaged, the rotation speed of the fourth rotation element Y4 is “1”, the rotation speed of the fifth rotation element Y5 is N2, and the third rotation element Y3 is “7th”. To establish the seventh gear.

  When the first brake B1 and the third brake B3 are engaged, the rotation speed of the fourth rotation element Y4 is “0”, the rotation speed of the fifth rotation element Y5 is N2, and the rotation speed of the third rotation element Y3 is The reverse speed is established by “Rev” of reverse rotation (reverse rotation).

  FIG. 7B collectively shows the engagement state of each engagement element at each shift stage described above, and “◯” represents engagement. 7B shows that the gear ratio i of the first planetary gear 6 is 2.328, the gear ratio j of the second planetary gear 7 is 2.935, the gear ratio k of the third planetary gear 8 is 1.914, Also shown are the gear ratios (rotational speed of the input shaft 2 / rotational speed of the output gear 3) when the gear ratio m of the planetary gear 41 is 1.600 and the gear ratio n of the fifth planetary gear 42 is 2.500. Yes. According to this, the common ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (ratio of the gear ratio of the first gear to the gear ratio of the seventh gear (the ratio of the first gear of FIG. 7B) Appropriate ratio))) is also appropriate.

  According to the automatic transmission of the fifth embodiment, all the elements of the sun gear Sc, the ring gear Rc, and the carrier Cc of the second planetary gear 7 are integrated with the elements of the first planetary gear 6 or the third planetary gear 8, and the double planetary gear 5 Is substantially constituted by the first and third planetary gears 6 and 8. Accordingly, the compound planetary gear 5 having the five rotary elements Y1 to Y5 can be configured without increasing the shaft length of the automatic transmission, and the common ratio of the automatic transmission can be reduced without impairing the mountability on the vehicle. The degree of freedom in setting (the ratio of gear ratios between gears) can be improved.

  In the automatic transmission of the fifth embodiment, even if the double planetary gear 5 is reversed left and right as in the relationship between the first embodiment and the second embodiment and the relationship between the third embodiment and the fourth embodiment. The same effect as that of the fifth embodiment is achieved.

DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output gear (output member), 41 ... 1st planetary gear, Sa1 ... Sun gear, Ra1 ... Ring gear, Ca1 ... Carrier, Pa1 ... Pinion, 42 ... 2nd planetary gear, Sa2 ... Sun gear, Ra2 ... ring gear, Ca2 ... carrier, Pa2 ... pinion, 5 ... double planetary gear, 6 ... first planetary gear, Sb ... sun gear, Rb ... ring gear, Cb ... carrier, Pb ... pinion (in the fifth embodiment, stepped pinion ), Pb1 ... small diameter portion, Pb2 ... large diameter portion, Pb '... pinion, 7 ... second planetary gear, Sc ... sun gear, Rc ... ring gear, Cc ... carrier, Pc ... pinion, 8 ... third planetary gear, Sd ... sun gear, Rd ... Ring gear, Cd ... Carrier, Pd, Pd '... Pinion, Y1 ... First rotating element Y2 ... second rotating element, Y3 ... third rotating element, Y4 ... fourth rotating element, Y5 ... fifth rotating element, C1 ... first clutch (first engaging element), C2 ... second clutch (second engaging) Combination element), C3 ... third clutch (sixth engagement element), B1 ... first brake (third engagement element), B2 ... second brake (fourth engagement element), B3 ... third brake (second engagement element) 5 engagement elements), F1 ... one-way clutch.

Claims (9)

An automatic transmission that shifts a plurality of stages through an input planetary gear concentrically arranged with the input shaft and a shift-type planetary gear and transmits the rotation to the output member.
The compound planetary gear includes a first planetary gear, a second planetary gear, and a third planetary gear.
The first and third planetary gears are each composed of a sun gear, a ring gear, and a carrier that meshes with each other and supports a pair of pinions, one of which meshes with the sun gear and the other meshes with the ring gear, so as to rotate and revolve.
The second planetary gear includes a sun gear, a ring gear, and a carrier that supports the sun gear and the pinion that meshes with the ring gear so as to rotate and revolve.
A pinion that meshes with the ring gear of the first planetary gear, a pinion of the second planetary gear, and a pinion that meshes with the sun gear of the third planetary gear are integrated,
An automatic transmission characterized in that a ring gear of a second planetary gear is integrated with a ring gear of a first planetary gear, and a sun gear of a second planetary gear is integrated with a sun gear of a third planetary gear. 2. The automatic transmission according to claim 1, further comprising fourth and fifth planetary gears for input, wherein each of the fourth and fifth planetary gears is connected to an input shaft and fixed to the transmission case. A fixed element and an output element configured to shift the rotation of the input shaft and output from the output element,
The sun gear, ring gear, and carrier elements of the first to third planetary gears of the compound planetary gear constitute five rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the speed diagram. The first rotating element, the second rotating element, the third rotating element, the fourth rotating element, and the fifth rotating element, respectively, as the first rotating element, second rotating element, third rotating element, fourth rotating element, and fifth rotating element in this order, the second rotating element is the fifth planetary gear output element The element and the third rotating element are connected to the output member,
As the engagement element, a first engagement element that can be switched between a state in which the first rotation element is connected to the input shaft and a state in which the connection is disconnected, and a state in which the fifth rotation element is connected to the input shaft and the connection are disconnected. A second engagement element that can be switched to a state, a third engagement element that can be switched between a state in which the fourth rotation element is fixed to the transmission case and a state in which the fixation is released, and a fixing element for the fourth planetary gear A fourth engaging element that can be switched between a state in which the gear is fixed to the transmission case and a state in which the fixing is released, a state in which the fixing element of the fifth planetary gear is fixed to the transmission case, and a state in which the fixing is released An automatic transmission comprising a switchable fifth engaging element.   3. The automatic transmission according to claim 2, wherein the fourth planetary gear for input increases the rotation of the input shaft input to the input element and outputs from the output element, and the fifth planetary gear for input is the input An automatic transmission characterized in that the rotation of an input shaft input to an element is decelerated and output from an output element. 2. The automatic transmission according to claim 1, further comprising a fourth planetary gear for input, wherein the fourth planetary gear includes an input element coupled to the input shaft, a fixed element fixed to the transmission case, and an output element. Is configured to shift the rotation of the input shaft and output from the output element,
The sun gear, ring gear, and carrier elements of the first to third planetary gears of the compound planetary gear constitute five rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the speed diagram. The first rotating element, the second rotating element, the third rotating element, the fourth rotating element, and the fifth rotating element, respectively, are connected to the output element of the fourth planetary gear and the fourth rotating element to the output member, respectively. And
As the engagement element, a first engagement element that can be switched between a state in which the first rotation element is connected to the input shaft and a state in which the connection is disconnected, and a state in which the fifth rotation element is connected to the input shaft and the connection are disconnected. A second engaging element that can be switched to a state, a third engaging element that can be switched between a state in which the third rotating element is fixed to the transmission case and a state in which the fixing is released, and a fixing element for the fourth planetary gear Can be switched between a state in which the first fixing element is fixed to the transmission case and a state in which the first rotation element is released. An automatic transmission comprising: a fifth engaging element; and a sixth engaging element switchable between a state in which the second rotating element is connected to the input shaft and a state in which the connection is broken.   5. The automatic transmission according to claim 4, wherein the fourth planetary gear for input speeds up rotation of the input shaft input to the input element and outputs it from the output element. An automatic transmission that shifts a plurality of stages through an input planetary gear concentrically arranged with the input shaft and a shift-type planetary gear and transmits the rotation to the output member.
The compound planetary gear includes a first planetary gear, a second planetary gear, and a third planetary gear.
The first and second planetary gears include a sun gear, a ring gear, and a carrier that supports the sun gear and the pinion meshing with the ring gear so as to rotate and revolve.
The third planetary gear is composed of a sun gear, a ring gear, and a carrier that meshes with each other and supports a pair of pinions, one meshed with the sun gear and the other meshed with the ring gear, so as to rotate and revolve.
Any one of the pinion of the first planetary gear, the pinion of the second planetary gear, and the pair of pinions of the third planetary gear is integrated,
The sun gear of the second planetary gear is integrated with the sun gear of the third planetary gear, the ring gear of the second planetary gear is integrated with the ring gear of the first planetary gear,
An automatic transmission characterized in that the gear ratio of the first planetary gear and the gear ratio of the second planetary gear are different from each other.   7. The automatic transmission according to claim 6, wherein the pinion of the first planetary gear is constituted by a stepped pinion having a large diameter portion and a small diameter portion having different numbers of teeth, and the sun gear of the first planetary gear is a stepped pinion. The ring gear of the first planetary gear meshes with either the large diameter portion or the small diameter portion of the stepped pinion, and the sun gear of the third planetary gear meshes with either the large diameter portion or the small diameter portion. The ring gear of the third planetary gear or the pinion meshing with this ring gear meshes with either the large diameter portion or the small diameter portion of the stepped pinion, and meshes with either the large diameter portion or the small diameter portion. An automatic transmission characterized in that the planetary gear pinion is configured by either the large-diameter portion or the small-diameter portion of the stepped pinion. 8. The automatic transmission according to claim 6, further comprising input fourth and fifth planetary gears, wherein each of the fourth and fifth planetary gears includes an input element coupled to the input shaft, and a speed change. A fixed element fixed to the machine case, and an output element, configured to shift the rotation of the input shaft and output from the output element;
The sun gear, ring gear and carrier elements of the first to third planetary gears of the double planetary gear constitute five rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the speed diagram. The first rotation element, the second rotation element, the third rotation element, the fourth rotation element, and the fifth rotation element, respectively, as the first rotation element, the second rotation element, the fourth rotation element, and the fifth rotation element, in turn, the fifth rotation element is the output of the fifth planetary gear. The element and the third rotating element are connected to the output member,
As the engagement element, a first engagement element that can be switched between a state in which the first rotation element is connected to the input shaft and a state in which the connection is disconnected, and a state in which the fourth rotation element is connected to the input shaft and the connection are disconnected. A second engagement element that can be switched to a state, a third engagement element that can be switched between a state in which the fourth rotation element is fixed to the transmission case and a state in which the fixation is released, and a fixing element for the fourth planetary gear A fourth engaging element that can be switched between a state in which the gear is fixed to the transmission case and a state in which the fixing is released, a state in which the fixing element of the fifth planetary gear is fixed to the transmission case, and a state in which the fixing is released An automatic transmission comprising a switchable fifth engaging element.   9. The automatic transmission according to claim 8, wherein the input fourth and fifth planetary gears reduce the rotation of the input shaft input to the input element and output from the output element, and the gear ratio of the fourth planetary gear. And the fifth planetary gear have different gear ratios.

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