JP5362598B2 - Automatic transmission - Google Patents

Automatic transmission Download PDF

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JP5362598B2
JP5362598B2 JP2010012533A JP2010012533A JP5362598B2 JP 5362598 B2 JP5362598 B2 JP 5362598B2 JP 2010012533 A JP2010012533 A JP 2010012533A JP 2010012533 A JP2010012533 A JP 2010012533A JP 5362598 B2 JP5362598 B2 JP 5362598B2
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element
planetary gear
gear mechanism
automatic transmission
brake
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JP2011149522A (en
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聡一 杉野
憲明 斉藤
晃平 飯塚
ジョエルグ・ミューラー
リコ・レッシュ
ミルコ・リーシュ
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本田技研工業株式会社
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission capable of reduced friction loss and improved mountability on a vehicle. <P>SOLUTION: The automatic transmission includes four planetary gear mechanisms 4-7, four first-fourth connectors Sa-Sc, Ca-Sb, Ra-Cb-Cd, Rc-Sd, and five engaging mechanisms C1, C2, B1-B3. The second connector Ca-Sb is connected to an input shaft 2, and a twelfth element Rd is connected to an output member 3. A first clutch C1 and a second clutch C2 connect the second connector Ca-Sb to an eighth element Cc and the third connector Ra-Cb-Cd to the eighth element Cc in a disconnectable manner, respectively. A first brake B1, a second brake B2 and a third brake B3 fix a sixth element Rd, the first connector Sa-Sc and the fourth connector Rc-Sd to a transmission case 1 in releasable manner, respectively. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to an automatic transmission that shifts the rotation of an input shaft to a plurality of stages via a plurality of planetary gear mechanisms arranged in a transmission case and outputs the result from an output member.

  2. Description of the Related Art Conventionally, there has been known an automatic transmission capable of performing eight forward gears using a first planetary gear mechanism for input, two planetary gear mechanisms for shifting, and six engaging mechanisms ( For example, see Patent Document 1).

  In Patent Document 1, a first planetary gear mechanism for input includes a first sun gear, a first ring gear, a pair of first gears that mesh with each other, one meshed with the first sun gear, and the other meshed with the first ring gear. It is composed of a double pinion type planetary gear mechanism comprising a first carrier that pivotally supports the pinion so as to rotate and revolve.

  The first planetary gear mechanism is configured to reduce the rotational speed of a first element that is fixed to a transmission case, a first element that is connected to an input shaft, and a first ring gear that is an input element. It is an output element to output.

  Further, the two planetary gear mechanisms for shifting are engaged with the second sun gear, the third sun gear, and the second ring gear integrated with the third ring gear, and one of them is engaged with the second sun gear and the second ring gear. The other is composed of a Ravigneaux type planetary gear mechanism comprising a second carrier that pivotally supports and revolves a pair of second pinions meshing with the third sun gear.

  This Ravigneaux type planetary gear mechanism has a first rotation element and a second rotation in order with an interval corresponding to the gear ratio in a speed diagram (a ratio of relative speeds of the respective rotation elements can be represented by a straight line). When the element, the third rotating element, and the fourth rotating element are used, the first rotating element is the second sun gear, the second rotating element is the second carrier integrated with the third carrier, and the third rotating element is integrated with the third ring gear. The converted second ring gear and fourth rotation element become the third sun gear.

  Also, as an engagement mechanism, a first wet multi-plate clutch that releasably connects a first ring gear that is an output element of the first planetary gear mechanism and a fourth rotation element that is a third sun gear, an input shaft, and a second carrier A second wet multi-plate clutch that releasably connects the second rotating element, and a third wet multi-plate clutch that releasably connects the first rotating element that is the output element and the first ring gear and the second sun gear. , A fourth wet multi-plate clutch for releasably connecting the first carrier as the input element and the first rotating element composed of the second sun gear, and the first rotating element composed of the second sun gear are releasably fixed to the transmission case. And a second brake for releasably fixing the second rotating element including the second carrier to the transmission case.

  According to the above configuration, the first speed is established by engaging the first wet multi-plate clutch and the second brake, and the second speed is established by engaging the first wet multi-plate clutch and the first brake. A stage is established, and a third speed stage is established by engaging the first wet multi-plate clutch and the third wet multi-plate clutch, and the first wet multi-plate clutch and the fourth wet multi-plate clutch are engaged. This establishes the fourth gear.

  Further, the fifth speed stage is established by engaging the first wet multi-plate clutch and the second wet multi-plate clutch, and 6 by engaging the second wet multi-plate clutch and the fourth wet multi-plate clutch. By establishing the first gear, engaging the second wet multi-plate clutch and the third wet multi-plate clutch, the seventh gear is established, and by engaging the second wet multi-plate clutch and the first brake. The eighth gear is established.

  In the third wet multi-plate clutch of Patent Document 1, the hydraulic chamber for operating the piston is arranged on the axis of the input shaft, but the plurality of clutch plates pressed by the piston are the input first. It is arranged radially outward of the one planetary gear mechanism.

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 are open increases, resulting in a problem that the efficiency of the automatic transmission deteriorates.

  Unlike the brake provided in the transmission case, the clutch is provided on the input shaft, the main shaft that supports the input shaft, and the like, and cannot be disposed radially outward of the planetary gear.

  Therefore, in the conventional example, a total of seven members including three planetary gear mechanisms and four clutches are arranged on the input shaft or on the main shaft that rotatably supports the input shaft. There is an inconvenience that the length becomes long and the mounting property to a vehicle (particularly, FF type vehicle) is low.

  In view of the above, an object of the present invention is to provide an automatic transmission that can reduce friction loss and can be mounted on a vehicle.

  [1] To achieve the above object, according to the present invention, an output member is provided by shifting the rotation of an input shaft that is rotatably supported in a transmission case and rotated by power from a drive source into a plurality of stages. The first to fourth planetary gear mechanisms each having three elements including a sun gear, a carrier, and a ring gear are provided, and the three elements of the first planetary gear mechanism are connected to a speed line. The first element, the second element, and the third element are arranged in the order corresponding to the gear ratio in the drawing, respectively, and the three elements of the second planetary gear mechanism are arranged in the speed chart corresponding to the gear ratio. The fourth element, the fifth element, and the sixth element are sequentially arranged, and the three elements of the third planetary gear mechanism are respectively arranged in the order corresponding to the gear ratio in the velocity diagram in the order of the seventh element and the eighth element. And the ninth element, and the three elements of the fourth planetary gear mechanism as the tenth element, the eleventh element, and the twelfth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, The seventh element is connected to form a first connection body, the second element and the fourth element are connected to form a second connection body, and the third element, the fifth element, and the A third connector is configured by connecting the eleventh element, a fourth connector is configured by connecting the ninth element and the tenth element, and the second connector is connected to the input shaft. A first clutch that is switchable between a connected state in which the twelfth element is connected to the output member, the second connected body and the eighth element are connected, and an open state in which the connection is broken; A connection state for connecting the connection body and the eighth element, and an opening for breaking the connection. A second clutch that can be switched to a state, a first brake that can be switched between a fixed state in which the sixth element is fixed to the transmission case, and an open state in which the fixing is released, and the first coupling body. A second brake that can be switched between a fixed state for fixing to the transmission case and an open state for releasing the fixing, a fixed state for fixing the fourth connecting body to the transmission case, and releasing the fixing. And a third brake switchable to an open state.

  According to the present invention, as will be apparent from the description of the embodiment described later, it is possible to perform eight forward shifts and at each shift stage among a total of five engagement mechanisms of two clutches and three brakes. Two engagement mechanisms will be engaged. For this reason, the number of engagement mechanisms opened at each shift stage is three, and the friction loss due to the opened engagement mechanisms is reduced as compared with the conventional one where four engagement mechanisms are opened. The transmission efficiency of the automatic transmission can be improved.

  Further, four planetary gear mechanisms and two clutches are arranged on the axis of the input shaft, and a total of six members are arranged. For this reason, the axial length of the automatic transmission can be shortened as compared with the conventional product in which a total of seven members of three planetary gear mechanisms and four clutches are arranged on the axis of the input shaft, The mounting property to a vehicle (especially FF type vehicle) can be improved.

  [2] In the present invention, a 1-way clutch that rotates integrally with the sixth element is provided only when the sixth element rotates in the reverse direction, and a fixed state in which the one-way clutch is fixed to the transmission case and the fixing are released. It is preferable to provide the 4th brake which can be switched to an open state.

  According to this, as will be apparent from the description of the embodiment described later, the first brake can be constituted by a wet multi-plate brake having a relatively small capacity, and the friction loss can be further reduced. In addition, the controllability of the shift between the shift speeds can be improved. Moreover, the 1-way clutch can be disabled by opening the fourth brake. Thereby, the reverse gear can be established.

  [3] In the present invention, the first brake is a dog clutch, or a reverse rotation preventing state in which the sixth element is allowed to rotate forward and the reverse rotation is prevented, and a forward rotation in which the sixth element is prevented from rotating forward and the reverse rotation is allowed. A two-way clutch that can be switched to a blocking state can also be used.

  According to this, the controllability of the shift is improved as will be apparent from the description of the embodiment described later. Further, in the open gear stage where the sixth element is not fixed to the transmission case by the 2-way clutch as the first brake, no friction loss occurs in the 2-way clutch as the first brake. For this reason, the friction loss can be further reduced as the entire automatic transmission.

  [4] In the present invention, each of the four planetary gear mechanisms is constituted by a single-pinion type planetary gear mechanism including a sun gear, a ring gear, and a carrier that rotatably and revolves a pinion that meshes with the sun gear and the ring gear. It is preferable.

  According to this, the planetary gear mechanism is a double pinion type 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. Compared to the case of the planetary gear mechanism, the number of gear meshes in the power transmission path from the input shaft to the output member can be reduced, and the transmission efficiency can be improved.

The skeleton figure which shows the upper half of the automatic transmission of embodiment of this invention. The speed diagram which shows ratio of the relative speed of each element of the 1st-4th planetary gear mechanism of the automatic transmission of embodiment. Explanatory drawing which shows the connection and the fixed state of each engagement mechanism in every gear stage of the automatic transmission of embodiment.

  FIG. 1 shows an upper half of an embodiment of an automatic transmission according to the present invention. An automatic transmission according to this embodiment includes an input shaft 2 rotatably supported in a transmission case 1 and connected to a power source such as an engine (not shown), and an output gear arranged concentrically with the input shaft 2. The output member 3 which consists of these is provided. 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, a first planetary gear mechanism 4, a second planetary gear mechanism 5, a third planetary gear mechanism 6, and a fourth planetary gear mechanism 7 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.

  Refer to the speed diagram of the first planetary gear mechanism 4 shown in the first stage (upper stage) from the top of FIG. 2 (the figure showing the ratio of the relative rotational speeds of the three elements of the sun gear, carrier, and ring gear as a straight line). Then, if the three elements Sa, Ca, Ra of the first planetary gear mechanism 4 are the first element, the second element, and the third element, respectively, from the left side in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, One 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 h: where the gear ratio of the first planetary gear mechanism 4 (number of teeth of the ring gear / number of teeth of the sun gear) is h: 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.

  Similar to the first planetary gear mechanism 4, the second planetary gear mechanism 5 is a single gear comprising 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. It is composed of a pinion type planetary gear mechanism.

  Referring to the speed diagram of the second planetary gear mechanism 5 shown in the first stage (upper stage) from the top of FIG. 2, the three elements Sb, Cb, Rb of the second planetary gear mechanism 5 are changed 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 at the corresponding intervals, the fourth element is the sun gear Sb, the fifth element is the carrier Cb, 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 i: 1 where i is the gear ratio of the second planetary gear mechanism 5.

  Similar to the first and second planetary gear mechanisms 4 and 5, the third planetary gear mechanism 6 is a carrier Cc that supports the sun gear Sc, the ring gear Rc, and the pinion Pc that meshes with the sun gear Sc and the ring gear Rc so as to freely rotate and revolve. It consists of a single pinion type planetary gear mechanism.

  Referring to the speed diagram of the third planetary gear mechanism 6 shown in the second stage (middle stage) from the top in FIG. 2, the three elements Sc, Cc, Rc of the third planetary gear mechanism 6 are changed to the gear ratio in the speed diagram. If the seventh element, the eighth element, and the ninth element are arranged from the left side in the order of arrangement at the corresponding intervals, the seventh element is the sun gear Sc, the eighth element is the carrier Cc, and the ninth element is the ring gear Rc. 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 j: 1 where j is the gear ratio of the third planetary gear mechanism 6.

  Similar to the first to third planetary gear mechanisms 4 to 6, the fourth planetary gear mechanism 7 is a carrier Cd that supports the sun gear Sd, the ring gear Rd, and the pinion Pd that meshes with the sun gear Sd and the ring gear Rd so as to rotate and revolve. It consists of a single pinion type planetary gear mechanism.

  Referring to the speed diagram of the fourth planetary gear mechanism 7 shown in the third stage (lower stage) from the top in FIG. 2, the three elements Sd, Cd, Rd of the fourth planetary gear mechanism 7 are changed to the gear ratio in the speed diagram. Assuming that the tenth, eleventh and twelfth elements are arranged from left to right in the order of corresponding intervals, the tenth element is the sun gear Sd, the eleventh element is the carrier Cd, and the twelfth element is the ring gear Rd. The ratio between the distance between the sun gear Sd and the carrier Cd and the distance between the carrier Cd and the ring gear Rd is set to k: 1 where k is the gear ratio of the fourth planetary gear mechanism 7.

  Further, in the automatic transmission according to the embodiment, the sun gear Sa (first element) of the first planetary gear mechanism 4 and the sun gear Sc (seventh element) of the third planetary gear mechanism 6 are coupled to each other, and the first coupling body Sa-Sc. Is configured. Further, the carrier Ca (second element) of the first planetary gear mechanism 4 and the sun gear Sb (fourth element) of the second planetary gear mechanism 5 are connected to constitute a second connected body Ca-Sb.

  The ring gear Ra (third element) of the first planetary gear mechanism 4, the carrier Cb (fifth element) of the second planetary gear mechanism 5, and the carrier Cd (eleventh element) of the fourth planetary gear mechanism 7 are connected to each other. A three-linked body Ra-Cb-Cd is configured. Further, the ring gear Rc (9th element) of the third planetary gear mechanism 6 and the sun gear Sd (10th element) of the fourth planetary gear mechanism 7 are connected to form a fourth connected body Rc-Sd.

  The second connecting body Ca-Sb is connected to the input shaft 2, and the ring gear Rd (the twelfth element) of the fourth planetary gear mechanism 7 is connected to the output member 3.

  In the first planetary gear mechanism 4 and the second planetary gear mechanism 5, the carrier Ca (second element) and the sun gear Sb (fourth element) are connected, and the ring gear Ra (third element) and the carrier Cb (fifth element) are connected. Therefore, as shown in the upper part of FIG. 2, the ratio of the relative rotational speeds of the elements of the planetary gear mechanisms 4 and 5 can be represented by one speed diagram. For this reason, the first planetary gear mechanism 4 and the second planetary gear mechanism 5 constitute four rotating elements.

  Referring to the speed diagram shown in the upper part of FIG. 2, the first rotating element Y1, the second rotating element Y2, and the third rotating element are arranged from the left side in the order in which the rotating elements are arranged at intervals corresponding to the gear ratio in the speed diagram. Assuming that the element Y3 and the fourth rotating element Y4 are used, the first rotating element Y1 is a sun gear Sa (first element) that is a component of the first connecting body Sa-Sc, and the second rotating element Y2 is a second connecting body Ca-Sb, The third rotating element Y3 is a ring gear Ra and a carrier Cb as constituent elements of the third coupling body Ra-Cb-Cd, and the fourth rotating element Y4 is a ring gear Rb (sixth element).

  Then, the distance between the first rotation element Y1 and the second rotation element Y2, the distance between the second rotation element Y2 and the third rotation element Y3, and the distance between the third rotation element Y3 and the fourth rotation element Y4. The ratio is hi: i: 1.

  In the automatic transmission of the embodiment, the ring gears of the first connected body Sa-Sc, the second connected body Ca-Sb, the third connected body Ra-Cb-Cd, and the second planetary gear mechanism 5 are provided by the four planetary gear mechanisms 4-7. Rb (sixth element), carrier Cc (eighth element) of third planetary gear mechanism 6, fourth connector Rc-Sd, and ring gear Rd (twelfth element) of fourth planetary gear mechanism 7 constitute a total of seven rotating bodies. Has been.

  The automatic transmission according to the embodiment includes, as engagement mechanisms, first and second two wet multi-plate clutches C1 and C2, first to fourth four wet multi-plate brakes B1 to B4, 1 And a way clutch F1.

  The first wet multi-plate clutch C1 is configured to be switchable between a connected state in which the second connected body Ca-Sb and the carrier Cc (eighth element) of the third planetary gear mechanism 6 are connected and an open state in which the connection is broken. Has been. The second wet multi-plate clutch C2 can be switched between a connected state in which the third connected body Ra-Cb-Cd and the carrier Cc (eighth element) of the third planetary gear mechanism 6 are connected, and an open state in which this connection is cut off. It is configured.

  The first wet multi-plate brake B1 is configured to be switchable between a fixed state in which the ring gear Rb (sixth element) of the second planetary gear mechanism 5 is fixed to the transmission case 1 and an open state in which this fixing is released. . The second wet multi-plate brake B2 is configured to be switchable between a fixed state in which the first connecting body Sa-Sc is fixed to the transmission case 1 and an open state in which the fixing is released.

  The third wet multi-plate brake B3 is configured to be switchable between a fixed state in which the fourth connecting body Rc-Sd is fixed to the transmission case 1 and an open state in which this fixing is released. The fourth wet multi-plate brake B4 is configured to be switchable between a fixed state in which the 1-way clutch F1 is fixed to the transmission case 1 and an open state in which this fixing is released.

  The one-way clutch F1 rotates integrally with the ring gear Rb (sixth element) when the ring gear Rb (sixth element) of the second planetary gear mechanism 5 rotates in the reverse direction (rotation in the direction in which the vehicle moves backward). When Rb (sixth element) rotates in the forward direction (rotation in the direction in which the vehicle moves forward), it is configured to be relatively rotatable without rotating integrally with the ring gear Rb (sixth element).

  In the automatic transmission according to the embodiment, when the first gear is established, the first wet multi-plate clutch C1 is brought into a connected state and the fourth wet multi-plate brake B4 is brought into a fixed state. Thereby, 2nd coupling body Ca-Sb and the carrier Cc (8th element) of the 3rd planetary gear mechanism 6 rotate at "1" which is the same speed.

  In addition, the 1-way clutch F1 is fixed to the transmission case 1, and the reverse rotation of the ring gear Rb (sixth element) of the second planetary gear mechanism 5 is prevented by the action of the one-way clutch F1, and the ring gear Rb (sixth element) ) Becomes “0”. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “1st” shown in FIG. 2, and the first gear is established.

  At the first speed, the first wet multi-plate brake B1 is released, but the rotational speed of the ring gear Rb (sixth element) of the second planetary gear mechanism 5 becomes “0” by the action of the one-way clutch F1. Therefore, no friction loss occurs in the first wet multi-plate brake B1. Further, if the first wet multi-plate brake B1 is fixed at the first speed, the engine brake can be applied.

  When the second gear is established, the third wet multi-plate brake B3 and the fourth wet multi-plate brake B4 are fixed. As a result, the rotational speed of the fourth coupling body Rc-Sd becomes “0”, and the rotational speed of the ring gear Rb (sixth element) of the second planetary gear mechanism 5 also becomes “0” by the action of the one-way clutch F1. . Then, the rotation speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “2nd” shown in FIG.

  In the second speed stage, as in the case of the first speed stage, no friction loss occurs in the first wet multi-plate brake B1 that is in the released state. Even at the second speed, the engine brake can be applied if the first wet multi-plate brake B1 is set in a fixed state.

  When the third speed is established, the second wet multi-plate clutch C2 is brought into a connected state and the fourth wet multi-plate brake B4 is brought into a fixed state. As a result, the third connected body Ra-Cb-Cd and the carrier Cc (eighth element) of the third planetary gear mechanism 8 rotate at the same speed. Further, the rotation speed of the ring gear Rb (sixth element) of the second planetary gear mechanism 5 becomes “0” by the action of the one-way clutch F1. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “3rd” shown in FIG.

  In the third speed, as in the case of the first and second speeds, no friction loss occurs in the first wet multi-plate brake B1 in the open state. Even at the third speed, if the first wet multi-plate brake B1 is in a fixed state, the engine brake can be applied.

  When the fourth speed is established, the second wet multi-plate clutch C2 is brought into a connected state, and the third wet multi-plate brake B3 and the fourth wet multi-plate brake B4 are brought into a fixed state. As a result, the third connected body Ra-Cb-Cd and the carrier Cc (eighth element) of the third planetary gear mechanism 8 rotate at the same speed, and the rotational speed of the fourth connected body Rc-Sd becomes “0”. Become. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “4th” shown in FIG. 2, and the fourth speed stage is established.

  When the fifth gear is established, the first wet multi-plate clutch C1 and the second wet multi-plate clutch C2 are connected, and the fourth wet multi-plate brake B4 is fixed. As a result, the second connected body Ca-Sb, the carrier Cc (eighth element) of the third planetary gear mechanism 6 and the third connected body Ra-Cb-Cd rotate at “1” which is the same speed. And each element of all the planetary gear mechanisms 4-7 will be in the locked state which cannot be relatively rotated, and the rotational speed of the ring gear Rd (12th element) of the 4th planetary gear mechanism 7 connected with the output member 3 is "1". "5th" is reached, and the fifth gear is established.

  When the sixth speed is established, the second wet multi-plate clutch C2 is brought into a connected state, and the second wet multi-plate brake B2 and the fourth wet multi-plate brake B4 are brought into a fixed state. As a result, the third connected body Ra-Cb-Cd and the carrier Cc (eighth element) of the third planetary gear mechanism 8 rotate at the same speed, and the rotational speed of the first connected body Sa-Sc becomes “0”. Become. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “6th” shown in FIG.

  When the seventh gear is established, the first wet multi-plate clutch C1 is brought into a connected state, and the second wet multi-plate brake B2 and the fourth wet multi-plate brake B4 are brought into a fixed state. As a result, the second connected body Ca-Sb and the carrier Cc (eighth element) of the third planetary gear mechanism 6 rotate at the same speed “1”, and the rotational speed of the first connected body Sa-Sc becomes “0”. "become. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “7th” shown in FIG. 2, and the seventh speed stage is established.

  When the eighth speed is established, the second wet multi-plate brake B2, the third wet multi-plate brake B3, and the fourth wet multi-plate brake B4 are fixed. As a result, the rotation speeds of the first connected body Sa-Sc and the fourth connected body Rc-Sd become “0”. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes “8th” shown in FIG.

  When the reverse gear is established, the first wet multi-plate clutch C1 is brought into a connected state and the third wet multi-plate brake B3 is brought into a fixed state. Since the fourth wet multi-plate brake B4 is in the released state, the function of the one-way clutch F1 becomes invalid, and the ring gear Rb (sixth element) of the second planetary gear mechanism 5 is allowed to reversely rotate.

  Further, the second connected body Ca-Sb and the carrier Cc (eighth element) of the third planetary gear mechanism 6 rotate at the same speed “1”, and the rotational speed of the fourth connected body Rc-Sd is “0”. become. Then, the rotational speed of the ring gear Rd (12th element) of the fourth planetary gear mechanism 7 connected to the output member 3 becomes the reverse rotation “Rvs” shown 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 gear mechanism rotates following the planetary gear mechanism that transmits power among the four planetary gear mechanisms 4 to 7.

  FIG. 3A is a diagram collectively showing the relationship between the above-described shift speeds and the states of the clutches C1 and C2 and the brakes B1 to B4 and the one-way clutch F1 that are the respective engagement mechanisms. And “◯” in the columns of the brakes B1 to B4 indicate a connected state or a fixed state. Further, “◯” in the column of the 1-way clutch F1 indicates that the rotational speed of the second coupling body Ra-Cb is “0” due to the action of the 1-way clutch F1. Further, “(◯)” in the column of the first wet multi-plate brake B1 indicates that the engine brake is fixed when it is applied.

  3B, the gear ratio h of the first planetary gear mechanism 4 is 1.666, the gear ratio i of the second planetary gear mechanism 5 is 2.000, and the gear ratio j of the third planetary gear mechanism 6 is FIG. 3 (a) also shows the gear ratios (rotational speed of the input shaft 2 / rotational speed of the output member 3) of each gear when the gear ratio k of the second planetary gear mechanism 7 is 2.333 and 3.333. Yes. According to this, the public ratio (ratio of gear ratios between the gears) becomes appropriate, and the ratio orange (1st speed ratio / 8th speed ratio) shown in FIG. 3B is also appropriate.

  According to the automatic transmission of the embodiment, it is possible to perform eight forward shifts. In addition, from the fourth forward speed to the eighth forward speed, three engagement mechanisms out of a total of six engagement mechanisms of the two wet multi-plate clutches C1 and C2 and the four wet multi-plate brakes B1 to B4 are engaged. Will do. In addition, from the first forward speed to the third forward speed, the ring gear Ra (third element) of the first planetary gear mechanism 4 is operated by the one-way clutch F1 even if the first wet multi-plate brake B1 is in the released state. Since the rotational speed is “0”, no friction loss occurs in the first wet multi-plate brake B1.

  Therefore, the number of engagement mechanisms in which friction loss occurs at each gear speed except the reverse speed is three, as compared to the conventional mechanism in which four engagement mechanisms generate friction loss at each gear speed, Friction loss due to the open engagement mechanism can be reduced, and the transmission efficiency of the automatic transmission is improved.

  Further, on the axis of the input shaft 2 (or a main shaft (not shown) that rotatably supports the input shaft 2), a total of six planetary gear mechanisms 4 to 7 and two wet multi-plate clutches C1 and C2 are provided. Two members are arranged. For this reason, the shaft length of the automatic transmission is shortened as compared with the conventional product in which a total of seven members including three planetary gear mechanisms and four wet multi-plate clutches are arranged on the axis of the input shaft 2. It is possible to improve the mountability to a vehicle (particularly, FF type vehicle).

  Further, since all of the first to fourth planetary gear mechanisms 4 to 7 are constituted by a single pinion type planetary gear mechanism, each planetary gear mechanism 4 to 7 meshes with the sun gear and the ring gear and Compared to the case of a planetary gear mechanism of a double pinion type comprising a pair of pinions that mesh with the sun gear and the other mesh with the ring gear, and a carrier that rotatably and revolves, the input shaft 2 to the output member 3 The number of gear engagements in the power transmission path can be reduced, and transmission efficiency can be improved.

  In the automatic transmission of the embodiment, the effects of the above-described embodiment can be obtained even if the fourth wet multi-plate brake B4 and the one-way clutch F1 are omitted. In this case, from the first forward speed to the third forward speed, the first wet multi-plate brake B1 may be fixed.

  If the fourth wet multi-plate brake B4 and the 1-way clutch F1 are omitted as described above, the first wet multi-plate brake B1 is released when upshifting from the third speed to the fourth speed. In addition to switching to the state, it is necessary to switch the third wet multi-plate brake B3 to the fixed state. Further, when downshifting from the fourth speed stage to the third speed stage, it is necessary to switch the first wet multi-plate brake B1 to a fixed state and switch the third wet multi-plate brake B3 to an open state.

  In the automatic transmission according to the embodiment, when upshifting from the third speed to the fourth speed, it is only necessary to switch the third wet multi-plate brake B3 to a fixed state, and to reduce the speed from the fourth speed to the third speed. When shifting, it is only necessary to switch the third wet multi-plate brake B3 to the open state.

  Therefore, according to the automatic transmission of the embodiment, the fourth wet multi-plate brake B4 and the one-way clutch F1 are omitted, and the first and second gears are shifted during the shift between the third speed and the fourth speed. The controllability of shifting between the third speed stage and the fourth speed stage can be improved as compared with the case where it is necessary to switch the states of the two wet multi-plate brakes B1, B3.

  In addition, the first wet multi-plate brake B1 of the embodiment can be switched to a fixed state only when the engine brake is applied at the first to third gears, and thus is configured with a wet multi-plate brake having a relatively small capacity. be able to.

  Here, in the wet multi-plate brake, the friction loss generated in the open state increases in proportion to the increase in capacity. For this reason, according to the automatic transmission of the embodiment, as compared with the one that needs to use a wet multi-plate brake having a relatively large capacity, the fourth to eighth gears at which the fourth coupled body Cb-Rc rotates in the forward direction The friction loss generated in the first wet multi-plate brake B1 can be reduced, and the transmission efficiency can be further improved.

  In the embodiment, the first wet multi-plate brake B1 is used as the first brake of the present invention. However, the first brake of the present invention is not limited to this. For example, a meshing mechanism such as a dog clutch or a synchromesh mechanism, A two-way clutch may be used. If comprised in this way, the friction loss in a 1st brake can be suppressed more in the forward 4th speed level-8th speed level in which a 1st brake will be in an open state, and the transmission efficiency of an automatic transmission will be improved more. be able to.

  When a two-way clutch is used as the first brake, a reverse rotation prevention state in which forward rotation (rotation in the direction in which the vehicle moves forward) is allowed and reverse rotation (rotation in the direction in which the vehicle moves backward) is prevented in the forward gear. In the reverse stage, it is sufficient to switch to a forward rotation prevention state that prevents forward rotation and allows reverse rotation. In this case, the 1-way clutch F1 and the fourth wet multi-plate brake B4 can be omitted.

  According to this, the controllability of the shift between the third speed and the fourth speed can be improved for the same reason as when the 1-way clutch F1 of the automatic transmission according to the embodiment is used. The two-way clutch is a friction even when the ring gear Rb (sixth element) of the second planetary gear mechanism 5 is released from being fixed to the transmission case 1 (in the embodiment, the fourth speed to the eighth speed). There is no loss. For this reason, the friction loss can be further suppressed as the entire automatic transmission. Further, when the vehicle is in a decelerating state at the first to third forward speeds, the engine brake can be applied by switching the two-way clutch to the forward rotation preventing state.

  In the embodiment, the first to fourth planetary gear mechanisms 4 to 7 are configured by a single pinion type planetary gear mechanism. However, the first to fourth planetary gear mechanisms 4 to 7 are configured by a double pinion type planetary gear mechanism. May be.

DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output member, 4 ... 1st planetary gear mechanism, Sa ... Sun gear (1st element), Ra ... Ring gear (3rd element), Pa ... Pinion, Ca ... Carrier (1st) 2 elements), 5 ... second planetary gear mechanism, Sb ... sun gear (fourth element), Rb ... ring gear (sixth element), Pb ... pinion, Cb ... carrier (fifth element), 6 ... third planetary gear mechanism, Sc ... sun gear (seventh element), Rc ... ring gear (ninth element), Pc ... pinion, Cc ... carrier (eighth element), 7 ... fourth planetary gear mechanism, Sd ... sun gear (tenth element), Rd ... ring gear ( 12th element), Pd ... pinion, Cd ... carrier (11th element), C1 ... first wet multi-plate clutch (first clutch), C2 ... second wet multi-plate clutch (second clutch), B1 ... first Wet multi-plate brake (first brake), B2 ... Second wet multi-plate brake (second brake), B3 ... Third wet multi-plate brake (third brake), B4 ... Fourth wet multi-plate brake (fourth brake) ), F1 ... 1-way clutch.

Claims (4)

  1. An automatic transmission that is rotatably supported in a transmission case and that rotates the input shaft rotated by power from a drive source in multiple stages and outputs it from an output member,
    There are provided first to fourth planetary gear mechanisms each having three elements including a sun gear, a carrier, and a ring gear,
    The three elements of the first planetary gear mechanism are a first element, a second element, and a third element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
    The three elements of the second planetary gear mechanism are a fourth element, a fifth element, and a sixth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
    The three elements of the third planetary gear mechanism are a seventh element, an eighth element, and a ninth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
    The three elements of the fourth planetary gear mechanism are respectively arranged as a tenth element, an eleventh element, and a twelfth element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram.
    The first element and the seventh element are connected to form a first connection body, the second element and the fourth element are connected to form a second connection body, and the third element and the The fifth element and the eleventh element are connected to form a third connecting body, the ninth element and the tenth element are connected to form a fourth connecting body,
    The second connector is connected to the input shaft, the twelfth element is connected to the output member,
    A first clutch that is switchable between a connected state for connecting the second connecting body and the eighth element, and an open state for disconnecting the connection;
    A second clutch that is switchable between a connected state that connects the third connecting body and the eighth element, and an open state that cuts off the connection;
    A first brake that is switchable between a fixed state for fixing the sixth element to the transmission case and an open state for releasing the fixing;
    A second brake switchable between a fixed state for fixing the first coupling body to the transmission case and an open state for releasing the fixing;
    An automatic transmission comprising: a third brake switchable between a fixed state in which the fourth connecting body is fixed to the transmission case and an open state in which the fixing is released.
  2. The automatic transmission according to claim 1, wherein
    Only when the sixth element reverses, a 1-way clutch that rotates integrally with the sixth element is provided,
    4. An automatic transmission comprising a fourth brake capable of switching between a fixed state in which the one-way clutch is fixed to the transmission case and an open state in which the fixing is released.
  3. The automatic transmission according to claim 1, wherein
    The first brake switches between a dog clutch or a reverse rotation preventing state in which forward rotation of the sixth element is allowed and reverse rotation is prevented, and a forward rotation prevention state in which forward rotation of the sixth element is prevented and reverse rotation is allowed. An automatic transmission comprising a free two-way clutch.
  4. The automatic transmission according to any one of claims 1 to 3,
    The four planetary gear mechanisms are constituted by a single pinion type planetary gear mechanism including a sun gear, a ring gear, and a carrier that rotatably and revolves a pinion that meshes with the sun gear and the ring gear. Automatic transmission.
JP2010012533A 2010-01-22 2010-01-22 Automatic transmission Active JP5362598B2 (en)

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Cited By (2)

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KR102048911B1 (en) * 2018-07-25 2019-11-26 안동대학교 산학협력단 Multistage auto-transmission apparatus of vehicles using dog clutch
KR102048910B1 (en) * 2018-07-04 2019-11-26 안동대학교 산학협력단 Multistage auto-transmission apparatus of vehicles using dog clutch

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JP5987368B2 (en) 2011-07-05 2016-09-07 株式会社リコー Illumination device and projection device
KR101371716B1 (en) * 2011-09-29 2014-03-10 현대자동차(주) Auto transmission for vehicle
JP5479518B2 (en) * 2012-03-13 2014-04-23 本田技研工業株式会社 Automatic transmission
JPWO2013146030A1 (en) * 2012-03-28 2015-12-10 アイシン・エィ・ダブリュ株式会社 Automatic transmission device
JP5651199B2 (en) 2013-01-31 2015-01-07 本田技研工業株式会社 Automatic transmission
JP6036642B2 (en) * 2013-10-28 2016-11-30 マツダ株式会社 Automatic transmission

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JPH0932919A (en) * 1995-07-17 1997-02-07 Jatco Corp Friction engagement device for automatic transmission
JP2005030430A (en) * 2003-07-07 2005-02-03 Fuji Heavy Ind Ltd Transmission for electric vehicle
JP4852933B2 (en) * 2004-12-28 2012-01-11 トヨタ自動車株式会社 Multistage transmission for vehicles
JP4380573B2 (en) * 2005-03-25 2009-12-09 トヨタ自動車株式会社 Multistage transmission for vehicles
JP4736655B2 (en) * 2005-09-09 2011-07-27 トヨタ自動車株式会社 Multistage transmission for vehicles

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KR102048910B1 (en) * 2018-07-04 2019-11-26 안동대학교 산학협력단 Multistage auto-transmission apparatus of vehicles using dog clutch
KR102048911B1 (en) * 2018-07-25 2019-11-26 안동대학교 산학협력단 Multistage auto-transmission apparatus of vehicles using dog clutch

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