JP5317829B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission that shifts the rotation of an input shaft to a plurality of stages through a plurality of planetary gear mechanisms disposed in a transmission case and transmits the rotation to an output member.

  2. Description of the Related Art Conventionally, there has been known an automatic transmission that can perform eight forward speeds using a first planetary gear for input, two planetary gears for shifting, and six engagement mechanisms (for example, Patent Document 1).

  In Patent Document 1, a pair of first pinions in which a first planetary gear for input meshes with a first sun gear and a first ring gear, one meshes with the first sun gear and the other meshes with the first ring gear. Is constituted by a double pinion type planetary gear mechanism comprising a first carrier that pivotally supports and rotates freely.

  The first planetary gear decelerates the rotation speed of the first carrier, which is a fixed element that fixes the first sun gear to the transmission case, the input element that connects the first carrier to the input shaft, and the first carrier that serves as the input element. Output element to be

  Further, the two planetary gear mechanisms for shifting are meshed with the second sun gear, the third sun gear, and the second ring gear integrated with the third ring gear, and one meshes with the second sun gear and the second ring gear. The other is constituted by a Ravigneaux type planetary gear mechanism comprising a pair of second pinions meshing with the third sun gear and a second carrier that is pivotally supported to rotate and revolve.

  This Ravigneaux type planetary gear mechanism has a first rotating element, a second rotating element, a third rotating element, and a fourth rotating element in order at intervals corresponding to the gear ratio in the velocity diagram. Is the second sun gear, the second rotating element is the second carrier integrated with the third carrier, the third rotating element is the second ring gear integrated with the third ring gear, and the fourth rotating element is the third sun gear.

  In addition, as an engagement mechanism, a first engagement mechanism that releasably connects a first ring gear that is an output element of the first planetary gear and a fourth rotation element that is a third sun gear, a first engagement mechanism that includes an input shaft and a second carrier. A second engagement mechanism that releasably connects the two rotation elements, a third engagement mechanism that releasably connects the first ring element that is the output element and the first sun gear, and the input element A fourth engagement mechanism for releasably connecting the first carrier and the first rotating element composed of the second sun gear, and a fifth engagement for releasably fixing the first rotating element composed of the second sun gear to the transmission case A mechanism and a sixth engagement mechanism for releasably fixing the second rotating element including the second carrier to the transmission case.

  According to the above configuration, the first gear is established by engaging the first engagement mechanism and the sixth engagement mechanism, and the first engagement mechanism and the fifth engagement mechanism are engaged. The second gear is established, the third gear is established by engaging the first engagement mechanism and the third engagement mechanism, and the first engagement mechanism and the fourth engagement mechanism are engaged. 4th gear is established.

  Further, the fifth gear is established by engaging the first engagement mechanism and the second engagement mechanism, and the sixth gear is established by engaging the second engagement mechanism and the fourth engagement mechanism. The seventh gear is established by engaging the second engagement mechanism and the third engagement mechanism, and the eighth gear is established by engaging the second engagement mechanism and the fifth engagement mechanism. Is done. Alternatively, the first forward speed or the eighth speed can be eliminated to provide a forward seventh speed.

JP 2005-273768 A

  In the above-described conventional example, the number of engagement mechanisms engaged at each shift stage is two. Therefore, the friction loss due to dragging of the remaining four engagement mechanisms that have been released becomes large, and there is a problem that the efficiency of the transmission deteriorates.

  The present invention has been made in view of the above points, and an object thereof is to provide an automatic transmission capable of reducing friction loss.

To achieve the above object, the present invention provides an input shaft that is rotated by power from a drive source, and an automatic transmission that shifts the rotation of the input shaft to a plurality of shift speeds and outputs it from an output member. comprising from 1 to third three planetary gear mechanisms, the sun gear of the first planetary gear mechanism, one from each of the first element in the order of the three elements consisting of a carrier and a ring gear, at intervals corresponding to the gear ratio in the velocity diagram, the second element and third element, a sun gear of the second planetary gear mechanism, one from each fourth element in order of the three elements consisting of a carrier and a ring gear, at intervals corresponding to the gear ratio in the velocity diagram, the fifth element And the sixth element, and the three elements consisting of the sun gear, carrier and ring gear of the third planetary gear mechanism are arranged at intervals corresponding to the gear ratio in the velocity diagram. One from each seventh element in turn, as the eighth element and ninth element, the first element is connected to the input shaft, the seventh element is connected to the output member, first connects the third element and the fifth element A first engaging mechanism configured to connect the input shaft and the eighth element in a releasable manner; and a second element. A second engagement mechanism for releasably connecting the second element and the seventh element, a third engagement mechanism for releasably connecting the second element and the second connection body, and releasing the first connection body to the transmission case. A fourth engagement mechanism for freely fixing, a fifth engagement mechanism for releasably fixing the fourth element to the transmission case, and a sixth engagement mechanism for releasably fixing the eighth element to the transmission case. And the third planetary gear mechanism meshes with the sun gear and the ring gear, and one meshes with the sun gear while the other meshes with the other. It consists of a double-pinion type planetary gear mechanism comprising a pair of pinions meshing with the ring gear about its axis and revolve supported carriers, gear position connects the three any of six of the engaging mechanism, or established by fixing characterized Rukoto.

  According to the present invention, as will be apparent from the description of the embodiment to be described later, it is possible to perform a shift of seven or more forward speeds, and among the first to sixth engagement mechanisms, there are three The engagement mechanism is engaged. Therefore, the number of engagement mechanisms released at each shift stage is three, and the friction loss due to the released engagement mechanisms is reduced compared to the conventional one where four engagement mechanisms are released. This can reduce the transmission efficiency.

  In the present invention, it is preferable that the sixth engagement mechanism is constituted by a one-way clutch or a two-way clutch. According to such a configuration, the controllability of the shift between the first speed and the second speed can be improved as compared with the sixth engagement mechanism configured by only the wet multi-plate clutch.

  In the present invention, the second engagement mechanism is preferably a meshing mechanism. According to such a configuration, as will be apparent from the description of the embodiment described later, the second engagement mechanism that is engaged only in the forward-side low speed stage region and released only in the high speed stage region prevents the occurrence of friction loss. It is a meshing mechanism to prevent. For this reason, it is possible to further suppress the friction loss in the high speed region on the forward side, and to further improve the efficiency of the transmission.

  In the present invention, the third engagement mechanism is arranged on the radially outer side of the second engagement mechanism, and is configured to at least partially overlap the second engagement mechanism in the axial direction of the input shaft. It is preferable. According to this configuration, the shaft length of the transmission can be shortened.

The skeleton figure of 1st Embodiment of the automatic transmission of this invention. The speed diagram of the automatic transmission of 1st Embodiment. Explanatory drawing which shows collectively the engagement state of the engagement mechanism in each gear stage of the automatic transmission of 1st Embodiment. The skeleton figure which shows 2nd Embodiment of the automatic transmission of this invention. The skeleton figure which shows 3rd Embodiment of the automatic transmission of this invention.

  FIG. 1 shows a first embodiment of an automatic transmission according to the present invention. The automatic transmission according to the first embodiment is disposed concentrically with 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 member 3 composed of an output gear. The rotation of the output member 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 first planetary gear mechanism 4, the second planetary gear mechanism 5, and the third planetary gear mechanism 6 are disposed concentrically with the input shaft 2. The first planetary gear mechanism 4 is composed of a single pinion type planetary gear mechanism that includes a sun gear Sa, a ring gear Ra, and a carrier Ca that rotatably and revolves a pinion Pa that meshes with the sun gear Sa and the ring gear Ra. Yes.

  With reference to the speed diagram of the first planetary gear mechanism 4 shown in the upper part of FIG. 2 (the figure in which the rotational speeds of the three elements of the sun gear, the carrier, and the ring gear can be represented by straight lines), If the three elements consisting of the carrier Ca and the ring gear Ra are the first element, the second element, and the third element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, the first element is the sun gear Sa. The second element is the carrier Ca, and the third element is the ring gear Ra.

  Here, 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 i: the gear ratio of the first planetary gear mechanism 4 (the number of teeth of the ring gear / the number of teeth of the sun gear). Set to 1. In the velocity diagram, the lower horizontal line and the upper horizontal line indicate that the rotational speeds are “0” and “1” (the same rotational speed as the input shaft 2), respectively.

  The second planetary gear mechanism 5 includes a single pinion planetary gear mechanism including a sun gear Sb, a ring gear Rb, and a carrier Cb that rotatably and revolves a pinion Pb that meshes with the sun gear Sb and the ring gear Rb. .

Referring to the speed diagram of the second planetary gear mechanism 5 shown in the middle stage of FIG. 2, the three elements including the sun gear Sb, the carrier Cb, and the ring gear Rb of the second planetary gear mechanism 5 correspond to the gear ratio in the speed diagram. If the fourth element, the fifth element, and the sixth element are respectively arranged from the left side in the order of arrangement in the interval, the fourth element is the sun gear Sb, the fifth element is the carrier C b , and the sixth element is the ring gear Rb. The ratio between the distance between the sun gear Sb and the carrier Cb and the distance between the carrier Cb and the ring gear Rb is set to j: 1 where j is the gear ratio of the second planetary gear mechanism 5.

  The third planetary gear mechanism 6 includes a sun gear Sc and a ring gear Rc, and a carrier that rotatably supports a pair of pinions Pc and Pc ′ that mesh with each other and one meshes with the sun gear Sc and the other meshes with the ring gear Rc. It is composed of a double pinion type planetary gear mechanism composed of Cc.

  With reference to the speed diagram of the third planetary gear mechanism 6 shown in the lower part of FIG. 2, the three elements of the third planetary gear mechanism 6 including the sun gear Sc, the carrier Cc, and the ring gear Rc correspond to the gear ratio in the speed diagram. Assuming the seventh element, the eighth element, and the ninth element from the left side in the order of arrangement in the interval, the seventh element is the carrier Cc, the eighth element is the ring gear Rc, and the ninth element is the sun gear Sc. The ratio between the distance between the sun gear Sc and the carrier Cc and the distance between the carrier Cc and the ring gear Rc is set to k: 1, where k is the gear ratio of the third planetary gear mechanism 6.

  The sun gear Sa (first element) of the first planetary gear mechanism 4 is connected to the input shaft 2. The carrier Cc (seventh element) of the third planetary gear mechanism 6 is connected to the output member 3. Further, the ring gear Ra (third element) of the first planetary gear mechanism 4 and the carrier Cb (fifth element) of the second planetary gear mechanism 5 are connected to form the first connected bodies Ra and Cb. Further, the ring gear Rb (sixth element) of the second planetary gear mechanism 5 and the sun gear Sc (9th element) of the third planetary gear mechanism 6 are connected to form the second connecting bodies Rb and Sc.

  In the automatic transmission according to the first embodiment, the sun gear Sa (first element), the carrier Ca (second element), and the first coupling bodies Ra and Cb of the first planetary gear mechanism 4 are constituted by the three planetary gear mechanisms 4, 5, and 6. (Third and fifth elements), the sun gear Sb (fourth element) of the second planetary gear mechanism 5, the second coupling bodies Rb and Sc (sixth and ninth element), and the carrier Cc (seventh of the third planetary gear mechanism 6). Element) and ring gear Rc (eighth element) constitute a total of seven rotating bodies.

  The automatic transmission according to the first embodiment is a first mechanism that releasably connects the input shaft 2 and the ring gear Rc (eighth element) of the third planetary gear mechanism 6 as an engagement mechanism composed of a wet multi-plate clutch. The second clutch is a second engagement mechanism that releasably connects the first clutch C1, which is the combined mechanism, the carrier Ca (second element) of the first planetary gear mechanism 4 and the carrier Cc (seventh element) of the third planetary gear mechanism 6. A second clutch C2 and a third clutch as a third engagement mechanism for releasably connecting the carrier Ca (second element) of the first planetary gear mechanism 4 and the second coupling bodies Rb and Sc (sixth and ninth element). C3.

  The third clutch C3, which is the third engagement mechanism, is disposed radially outward of the second clutch C2, which is the second engagement mechanism, and overlaps with the second clutch C2 in the axial direction of the input shaft 2, whereby the transmission The shaft length of is shortened.

  Further, the automatic transmission according to the first embodiment is a first engagement body Ra, Cb (third and fifth elements) as an engagement mechanism composed of a wet multi-plate brake. A first brake B1 as a four engagement mechanism, a second brake B2 as a fifth engagement mechanism for releasably fixing the sun gear Sb (fourth element) of the second planetary gear mechanism 5 to the transmission case 1, and a third planetary gear. And a third brake B3 for releasably fixing the ring gear Rc (eighth element) of the mechanism 6 to the transmission case 1.

  In addition, the transmission case 1 permits forward rotation (rotation in the forward direction) of the ring gear Rc (eighth element) of the third planetary gear mechanism 6 in parallel with the third brake B3, and reverse rotation (rotation in the reverse direction). A 1-way clutch F1 is connected.

  In the automatic transmission according to the first embodiment, the third brake B3 and the one-way clutch F1 constitute the sixth engagement mechanism of the present invention.

  In the automatic transmission according to the first embodiment, when the second clutch C2 (second engagement mechanism) and the second brake B2 (fifth engagement mechanism) are engaged, the carrier Ca ( The second element) and the carrier Cc (seventh element) of the third planetary gear mechanism 6 rotate at the same rotational speed, and the rotational speed of the sun gear Sb (fourth element) of the second planetary gear mechanism 5 is “0”. The rotational speed of the ring gear Rc (eighth element) of the third planetary gear mechanism 6 becomes “0” by the action of the 1-way clutch F1, and the speed lines of the three planetary gear mechanisms 4, 5, 6 are indicated by “1st” in FIG. The first gear is established.

  At this time, the third brake B3 is released, but the rotational speed of the ring gear Rc (eighth element) of the third planetary gear mechanism 6 is “0” due to the action of the 1-way clutch F1, and therefore the third brake In B3, no friction loss occurs. Also, by providing the 1-way clutch F1, it is not necessary to supply the hydraulic pressure to the third brake B3 and stop the hydraulic pressure supply when shifting between the first gear and the second gear. The controllability of the shift between the first speed stage and the second speed stage can be improved.

  When the third brake B3 is engaged in addition to the second clutch C2 (second engagement mechanism) and the second brake B2 (fifth engagement mechanism), the first gear is set in a state where the engine brake can be applied. Established.

  When the second engagement mechanism C2, the fourth engagement mechanism B1, and the fifth engagement mechanism B2 are engaged, the rotation speed of the first coupling bodies Ra and Cb (third and fifth elements) is “0”. The rotational speed of the sun gear Sb (fourth element) of the second planetary gear mechanism 5 becomes “0”, and the three elements of the second planetary gear mechanism 5 enter a locked state in which the relative rotation is impossible, and the second coupling bodies Rb, Sc ( The rotation speed of the sixth and ninth elements is also “0”.

  Then, the carrier Ca (second element) of the first planetary gear mechanism 4 and the carrier Cc (seventh element) of the third planetary gear mechanism 6 rotate at the same rotational speed, and the speeds of the three planetary gear mechanisms 4, 5, 6 are increased. The line becomes a line indicated by “2nd” in FIG. 2, and the second gear is established.

  When the second engagement mechanism C2, the third engagement mechanism C3, and the fifth engagement mechanism B2 are engaged, the carrier Ca (second element) of the first planetary gear mechanism 4 and the second coupling bodies Rb, Sc (first 6, the ninth element) and the carrier Cc (seventh element) of the third planetary gear mechanism 6 rotate at the same rotational speed, and the three elements of the third planetary gear mechanism 6 including the sun gear Sc, the carrier Cc, and the ring gear Rc are relative to each other. It becomes a locked state that cannot be rotated. Then, the speed lines of the three planetary gear mechanisms 4, 5, 6 become lines indicated by “3rd” in FIG. 2, and the third speed stage is established.

  When the first engagement mechanism C1, the second engagement mechanism C2, and the fifth engagement mechanism B2 are engaged, the sun gear Sa (first element) of the first planetary gear mechanism 4 and the ring gear Rc ( The rotation speed with respect to the eighth element) becomes “1”, and the carrier Ca (second element) of the first planetary gear mechanism 4 and the carrier Cc (seventh element) of the third planetary gear mechanism 6 rotate at the same rotation speed. Thus, the speed lines of the three planetary gear mechanisms 4, 5, and 6 become lines indicated by "4th" in FIG. 2, and the fourth speed stage is established.

  When the first engagement mechanism C1, the second engagement mechanism C2, and the third engagement mechanism C3 are engaged, the sun gear Sa (first element) of the first planetary gear mechanism 4 and the ring gear Rc ( The rotation speed with respect to the eighth element) is “1”, the three elements of the sun planetary gear Sc, the carrier Cc, and the ring gear Rc of the third planetary gear mechanism 6 are locked so as not to be relatively rotatable, and are connected to the output member 3. A fifth gear stage in which the rotational speed of the carrier Cc of the three planetary gear mechanism 6 is also “1” is established.

  When the first engagement mechanism C1, the third engagement mechanism C3, and the fifth engagement mechanism B2 are engaged, the sun gear Sa (first element) of the first planetary gear mechanism 4 and the ring gear Rc of the third planetary gear mechanism 6 ( The rotational speed of the second planetary gear mechanism 5 is "0", the rotational speed of the sun gear Sb (fourth element) of the second planetary gear mechanism 5 is "0", and the carrier Ca (second element) of the first planetary gear mechanism 4 is The two connected bodies Rb, Sc rotate at the same rotational speed, and the speed lines of the three planetary gear mechanisms 4, 5, 6 become the lines indicated by "6th" in FIG. 2, and the sixth speed stage is established. .

  When the first engagement mechanism C1, the third engagement mechanism C3, and the fourth engagement mechanism B1 are engaged, the sun gear Sa (first element) of the first planetary gear mechanism 4 and the ring gear Rc of the third planetary gear mechanism 6 ( The rotation speed with respect to the eighth element) is "1", the rotation speed of the first coupling bodies Ra and Cb (third and fifth elements) is "0", and the carrier Ca (second element) of the first planetary gear mechanism 4 And the second coupling bodies Rb and Sc (sixth and ninth elements) rotate at the same rotational speed, and the speed lines of the three planetary gear mechanisms 4, 5, and 6 become the lines indicated by "7th" in FIG. Thus, the seventh gear is established.

  When the first engagement mechanism C1, the fourth engagement mechanism B1, and the fifth engagement mechanism B2 are engaged with each other, the sun gear Sa (first element) of the first planetary gear mechanism 4 and the ring gear Rc of the third planetary gear mechanism 6 ( The rotational speed of the second planetary gear mechanism 5 is "1", and the rotational speeds of the sun gear Sb (fourth element) and the first coupling bodies Ra and Cb (third and fifth elements) of the second planetary gear mechanism 5 are "0". Become.

  Then, the three elements of the second planetary gear mechanism 5 including the sun gear Sb, the carrier Cb, and the ring gear Rb are locked so as not to rotate relative to each other, and the rotational speed of the second coupling bodies Rb and Sc (sixth and ninth elements) is increased. The speed line of the three planetary gear mechanisms 4, 5, 6 becomes a line indicated by “8th” in FIG. 2, and the eighth speed stage is established.

  When the third engagement mechanism C3, the fifth engagement mechanism B2, and the sixth engagement mechanism B3 are engaged with each other, the sun gear Sb (fourth element) of the second planetary gear mechanism 5 and the ring gear Rc of the third planetary gear mechanism 6 ( The rotation speed of the eighth element) becomes “0”, and the carrier Ca (second element) of the first planetary gear mechanism 4 and the second coupling bodies Rb and Sc (sixth and ninth element) rotate at the same rotation speed. Then, the speed lines of the three planetary gear mechanisms 4, 5, and 6 become lines indicated by “Rev” in FIG. 2, and the reverse gear is established.

  A speed line indicated by a dotted line in FIG. 2 represents that each element of the other planetary gears rotates following the planetary gear that transmits power among the three planetary gear mechanisms 4, 5, and 6.

  FIG. 3 is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the engagement mechanisms C1 to C3 and B1 to B3, and “◯” represents engagement. FIG. 3 shows the case where the gear ratio i of the first planetary gear mechanism 4 is 1.666, the gear ratio j of the second planetary gear mechanism 5 is 1.666, and the gear ratio k of the third planetary gear mechanism 6 is 2.666. 4 also shows the gear ratio of each gear stage (the rotational speed of the input shaft 2 / the rotational speed of the output member 3). According to this, the common ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (1st speed ratio / 8th speed ratio) shown in the column of the 8th speed public ratio also becomes appropriate.

  According to the automatic transmission of the first embodiment, eight forward speeds can be changed, and three of the first to sixth engagement mechanisms C1 to C3 and B1 to B3 have three speeds. The engagement mechanism is engaged. Therefore, the number of engagement mechanisms released at each shift stage is three, and the friction loss due to the released engagement mechanisms is reduced compared to the conventional one where four engagement mechanisms are released. This can reduce the transmission efficiency.

  The automatic transmission according to the first embodiment has been described as performing eight forward speeds. However, by omitting any one speed, the automatic transmission is configured to perform seven forward speeds. Also good. For example, the seventh forward speed can be changed to the seventh forward speed by omitting the seventh speed of the first embodiment and changing the eighth speed to the seventh speed.

  In the automatic transmission according to the first embodiment, the first planetary gear mechanism 4 is configured by a single pinion type, but the first planetary gear mechanism 4 may be configured by a double pinion type. In this case, for example, the first element may be the sun gear Sa, the second element may be the ring gear Ra, and the third element may be the carrier Ca.

  Further, in the automatic transmission of the first embodiment, the second planetary gear mechanism 5 is configured by a single pinion type, but the second planetary gear mechanism 5 is similar to the automatic transmission of the second embodiment shown in FIG. 5 may be a double pinion type. In this case, for example, the fourth element may be the sun gear Sb, the fifth element may be the ring gear Rb, and the sixth element may be the carrier Cb.

  In the automatic transmission according to the first embodiment, the sixth engagement mechanism is configured by the third brake B3 and the one-way clutch F1, but is configured by only the third brake B3 without providing the one-way clutch F1. May be.

  Further, the sixth engagement mechanism allows reverse rotation (rotation in the forward direction) of the ring gear Rc (eighth element) of the third planetary gear mechanism 6 as in the automatic transmission of the third embodiment shown in FIG. A two-way clutch F2 that can be switched to a state that prevents (rotation in the reverse direction) or a state that prevents forward rotation of the ring gear Rc and allows reverse rotation may be used.

  Even in this case, as in the case where the one-way clutch F1 is provided, the controllability of the shift between the first gear and the second gear can be improved. Further, the third brake B3 having a relatively large capacity for the reverse gear can be omitted, the friction loss can be further reduced, and the transmission efficiency can be improved.

  Here, in the automatic transmission according to the third embodiment shown in FIG. 5, the second engagement mechanism is constituted by a dog clutch D1 (meshing mechanism). As is apparent from FIG. 3, the second engagement mechanism (the second clutch C2 in the first embodiment) is engaged at the first to fifth speed stages as the low speed stage area, and the sixth to eighth speeds as the high speed stage area. Opened in steps.

  Therefore, in the 1st to 5th speed stages, which are the low speed stage areas where the torque difference between the adjacent speed stages is large compared to the high speed area, the engagement state is not switched, and the 5th speed stage and the 6th speed stage having a relatively small torque difference. The engagement state is switched only when switching between the speed stages. For this reason, it is possible to smoothly shift between the fifth speed and the sixth speed.

  Further, since the dog clutch D1 is engaged by mechanical engagement and is not frictionally engaged unlike the wet multi-plate clutch, no friction loss occurs. For this reason, by configuring the second engagement mechanism with the dog clutch D1, the friction loss in the high speed range is higher than when the second engagement mechanism is configured with the wet multi-plate clutch C2 as in the first embodiment. Can be further reduced, and fuel consumption can be improved. The dog clutch D1 may be configured with a synchronization function such as a synchronization meshing mechanism (synchromesh mechanism).

DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output member (output gear), 4 ... 1st planetary gear mechanism, Sa ... Sun gear (1st element), Ca ... Carrier (2nd element), Ra ... Ring gear (1st 3 elements), 5 ... second planetary gear mechanism, Sb ... sun gear (fourth element), C b ... carrier (fifth element), Rb ... ring gear (sixth element), 6 ... third planetary gear mechanism, Sc ... sun gear ( Ninth element), Cc... Carrier (seventh element), Rc... Ring gear (eighth element).

Claims (4)

An input shaft that is rotated by power from a drive source, and an automatic transmission that shifts the rotation of the input shaft to a plurality of shift speeds and outputs it from an output member,
Comprising first to third planetary gear mechanisms;
The sun gear of the first planetary gear mechanism, the three elements consisting of a carrier and a ring gear, and from one to the order of at intervals corresponding to the gear ratio in the velocity diagram respectively a first element, a second element and a third element, the second planetary gear The three elements consisting of the sun gear, carrier and ring gear of the mechanism are arranged in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, from the one to the fourth element, the fifth element and the sixth element respectively, and the sun gear of the third planetary gear mechanism , The three elements consisting of the carrier and the ring gear are arranged as the seventh element, the eighth element, and the ninth element from the one side in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively.
The first element is connected to the input shaft, the seventh element is connected to the output member, the third element and the fifth element are connected to form the first connecting body, and the sixth element and the ninth element are connected. The second connector is configured,
A first engagement mechanism for releasably connecting the input shaft and the eighth element;
A second engagement mechanism for releasably connecting the second element and the seventh element;
A third engagement mechanism for releasably connecting the second element and the second connector,
A fourth engagement mechanism for releasably fixing the first connector to the transmission case;
A fifth engagement mechanism for releasably fixing the fourth element to the transmission case;
A sixth engagement mechanism for releasably fixing the eighth element to the transmission case,
The third planetary gear mechanism is a double-pinion type planetary gear mechanism comprising a sun gear, a ring gear, and a carrier that rotatably and revolves a pair of pinions that mesh with each other and one meshes with the sun gear and the other meshes with the ring gear. Consists of
Gear stage connected three any of six of the engagement mechanism or automatic transmission, wherein Rukoto established by fixing.   The automatic transmission according to claim 1, wherein the sixth engagement mechanism is a one-way clutch or a two-way clutch.   The automatic transmission according to claim 1, wherein the second engagement mechanism is a meshing mechanism.   The third engagement mechanism is disposed on a radially outer side of the second engagement mechanism, and at least a part of the third engagement mechanism overlaps with the second engagement mechanism in the axial direction of the input shaft. The automatic transmission according to any one of claims 1 to 3.

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