JP2010101404A - Automatic transmission - Google Patents

Automatic transmission Download PDF

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Publication number
JP2010101404A
JP2010101404A JP2008272912A JP2008272912A JP2010101404A JP 2010101404 A JP2010101404 A JP 2010101404A JP 2008272912 A JP2008272912 A JP 2008272912A JP 2008272912 A JP2008272912 A JP 2008272912A JP 2010101404 A JP2010101404 A JP 2010101404A
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Japan
Prior art keywords
gear
planetary gear
state
engagement
carrier
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JP2008272912A
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Japanese (ja)
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Noriaki Saito
憲明 斉藤
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Honda Motor Co Ltd
本田技研工業株式会社
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Priority to JP2008272912A priority Critical patent/JP2010101404A/en
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Abstract

An automatic transmission capable of reducing the number of clutches and disposing a brake radially outward of the clutch is provided.
An automatic transmission includes first to third planetary gears. The carrier Cf is connected to the input shaft 2 and the carrier Cr is connected to the output gear 3. A first engagement element C1 that connects the sun gear Sm and the input shaft 2, a second connection body Rm, Sr that connects the ring gear Rm and the sun gear Sr, and the input shaft 2 are connected via the carrier Cf. The transmission element 1 includes the coupling element C2, the third engagement element B1 that fixes the sun gear Sm to the transmission case 1, and the first coupling bodies Rf, Cm, and Rr that connect the ring gear Rf, the carrier Cm, and the ring gear Rr. A fourth engagement element B2 for fixing, a fifth engagement element B3 for fixing the second coupling bodies Rm, Sr to the transmission case 1, and a sixth engagement element B4 for fixing the sun gear Sf to the transmission case 1. Is provided.
[Selection] Figure 1

Description

  The present invention relates to an automatic transmission that shifts the rotation of an input member to a plurality of stages and transmits it to an output member.
  2. Description of the Related Art Conventionally, there is known an automatic transmission in which rotation of an input member is shifted to a plurality of stages and transmitted to an output member via a first planetary gear for input disposed in a transmission case and a double planetary gear for shifting ( For example, see Patent Document 1).
  In Patent Document 1, the first planetary gear 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)
  In the conventional example, there are four clutches and two brakes, and the number of clutches is larger than that of the brakes. Unlike the brake piston provided on the transmission case, the clutch piston is provided on the input shaft as the input member, the main shaft that supports the input shaft, and the like, and is disposed radially outward of the planetary gear. I can't. For this reason, when there are many clutches, there exists a malfunction that the axial length of an automatic transmission becomes long.
  Some brakes cannot be arranged radially outward of the planetary gear because of the configuration of the automatic transmission.
  In view of the above points, an object of the present invention is to provide an automatic transmission that can reduce the number of clutches and can dispose a brake radially outward of the clutch.
  To achieve the above object, according to a first aspect of the present invention, the rotation of an input member is shifted in a plurality of stages via a first planetary gear for input disposed in a transmission case and a double planetary gear for transmission. An automatic transmission for transmitting to an output member, wherein the compound planetary gear is composed of two second and third planetary gears, and the three elements including the sun gear, the carrier and the ring gear of the first planetary gear are shown in the velocity diagram. The first element, the second element, and the third element are arranged in the order corresponding to the gear ratio, and the three elements including the sun gear, the carrier, and the ring gear of the second planetary gear correspond to the gear ratio in the velocity diagram. The fourth element, the fifth element, and the sixth element are respectively arranged in the order of intervals, and three elements including the sun gear, the carrier, and the ring gear of the third planetary gear are provided. As the seventh element, the eighth element, and the ninth element in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram, the first element is configured by connecting the second element, the fifth element, and the seventh element. The input member is connected to the third element, the sixth element and the ninth element are connected to form a second connecting body, the eighth element is connected to the output member, and the fourth element and the input member A first engagement element that can be switched between a state in which the connection is cut off and a state in which the connection is cut off, and a second engagement that is switchable between a state in which the second connecting body and the input member are connected and a state in which the connection is cut off An element, a three-engagement element switchable between a state in which the fourth element is fixed to the transmission case and a state in which this fixing is released, a state in which the first coupling body is fixed to the transmission case, and this fixing is released A fourth engaging element that can be switched between a state and a state in which the second coupling body is fixed to the transmission case. A fifth engagement element that can be switched to a state of releasing the fixation, and a sixth engagement element that can be switched to a state of fixing the first element to the transmission case and a state of releasing the fixation. Features.
  According to the first aspect of the present invention, as will be apparent from the description of the embodiments described later, two clutches serving as the first and second engagement elements and four brakes serving as the third to sixth engagement elements. , 7 shifts forward can be performed. Further, the third engagement element is disposed radially outward of the first engagement element, the fourth engagement element is disposed radially outward of the double planetary gear, and the fifth engagement element is disposed in the second engagement element. Can be arranged radially outward. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the axial length of the automatic transmission can be shortened by disposing the brake radially outside the clutch or the planetary gear.
  According to a second aspect of the present invention, an automatic transmission that shifts the rotation of an input member to a plurality of stages via a first planetary gear for input disposed in a transmission case and a double planetary gear for transmission is transmitted to an output member. The compound planetary gear is composed of two planetary gears, a second planetary gear and a third planetary gear comprising a sun gear, a carrier, and a ring gear at intervals corresponding to the gear ratio in the velocity diagram. The first element, the second element, and the third element are arranged in the order of the three elements, and the three elements including the sun gear, the carrier, and the ring gear of the second planetary gear are arranged in the order corresponding to the gear ratio in the speed diagram. The four elements, the fifth element, and the sixth element, and the three elements including the sun gear, the carrier, and the ring gear of the third planetary gear, As the seventh element, the eighth element, and the ninth element, respectively, in order of arrangement at corresponding intervals, the first element is fixed to the transmission case, the input member is connected to the second element, the fifth element, the seventh element, Are connected to each other to form a first connecting body, and the sixth element and the ninth element are connected to form a second connecting body, and the eighth element is connected to the output member, and the third element and the fourth element are connected to each other. A first engagement element that can be switched between a state in which the elements are connected and a state in which the connection is cut off; a second state in which the connection is made between a state in which the third element and the second connection body are connected; The engaging element, three engaging elements that can be switched between a state in which the first connecting body and the input member are connected and a state in which the connection is cut off, a state in which the first connecting body is fixed to the transmission case, and this fixing A fourth engagement element that can be switched to a released state, a state in which the second coupling body is fixed to the transmission case, and this fixed element. A fifth engagement element that can be switched to a state in which the release is released, and a sixth engagement element that is switchable to a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released. And
  According to the second aspect of the present invention, as will be apparent from the description of the embodiment described later, the three clutches as the first to third engagement elements and the three brakes as the fourth to sixth engagement elements. , 7 shifts forward can be performed. In addition, the fourth engagement element can be disposed radially outward of the double planetary gear, and the fifth engagement element can be disposed radially outward of the second engagement element. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the axial length of the automatic transmission can be shortened by disposing the brake radially outside the clutch or the planetary gear.
  In the first and second aspects of the present invention, when the sixth element is a ring gear of the second planetary gear and the ninth element is a sun gear of the third planetary gear, the third planetary gear is radially outside of the second planetary gear. The shaft length of the automatic transmission can be made shorter by arranging the ring gear of the second planetary gear and the sun gear of the third planetary gear to form the second coupling body.
  In the first and second aspects of the present invention, if the fourth engagement element that is engaged only in the reverse gear, that is, is always released in the forward gear, is constituted by a dog clutch. Compared with a plate clutch, the friction loss associated with the release of the multi-plate clutch in the forward gear can be reduced, and the transmission efficiency can be improved.
  Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. In the first embodiment, an input shaft 2 that is rotatably supported in a transmission case 1 and that is connected to a power source such as an engine (not shown), and an output that is arranged concentrically with the input shaft 2. And an output gear 3 as a member. The rotation of the output gear 3 is transmitted to the left and right drive wheels of the vehicle via a differential gear (not shown).
  In the transmission case 1, an input first planetary gear 4 and a shift-type planetary gear 5 are arranged around the input shaft 2. The first planetary gear 4 includes a sun gear Sf, a ring gear Rf, and a carrier Cf that meshes with each other and supports a pair of pinions Pf and Pf ′ that mesh with the sun gear Sf and the other mesh with the ring gear Rf so as to rotate and revolve. It is composed of a double pinion type planetary gear.
  Referring to the velocity diagram of the first planetary gear 4 shown in the upper part of FIG. 2, three elements including the sun gear Sf, the carrier Cf, and the ring gear Rf of the first planetary gear 4 are separated by a distance corresponding to the gear ratio in the velocity diagram. If the first element, the second element, and the third element are arranged from the left side in the order in which they are arranged, the first element is the sun gear Sf, the second element is the ring gear Rf, and the third element is the carrier Cf. The ratio between the distance between the sun gear Sf and the carrier Cf and the distance between the carrier Cf and the ring gear Rf is set to i: 1 where i is the gear ratio of the first planetary gear 4 (number of teeth of the ring gear / number of teeth of the sun gear). Is set. The carrier Cf is connected to the input shaft 2. 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 compound planetary gear 5 includes a second planetary gear 6 and a third planetary gear 7. The second planetary gear 6 is composed of a single planetary gear comprising a sun gear Sm, a ring gear Rm, and a carrier Cm that supports the pinion Pm meshing with the sun gear Sm and the ring gear Rm so as to rotate and revolve. 7 is also composed of a single pinion type planetary gear comprising a sun gear Sr, a ring gear Rr, and a carrier Cr that supports the pinion Pr meshing with the sun gear Sr and the ring gear Rr so as to rotate and revolve.
  Referring to the speed diagram of the compound planetary gear 5 shown in the lower part of FIG. 2, the three elements including the sun gear Sm, the carrier Cm, and the ring gear Rm of the second planetary gear 6 are arranged at intervals corresponding to the gear ratio in the speed diagram. The fourth element is the sun gear Sm, the fifth element is the carrier Cm, and the sixth element is the ring gear Rm. The ratio between the distance between the sun gear Sm and the carrier Cm and the distance between the carrier Cm and the ring gear Rm is set to j: 1 where j is the gear ratio of the second planetary gear 6.
  Further, referring to the velocity diagram of the compound planetary gear 5, the three elements including the sun gear Sr, the carrier Cr and the ring gear Rr of the third planetary gear 7 are arranged in the order corresponding to the gear ratio in the velocity diagram. Assuming that the seventh element, the eighth element, and the ninth element are the left side, the seventh element is the ring gear Rr, the eighth element is the carrier Cr, and the ninth element is the sun gear Sr. The ratio between the distance between the sun gear Sr (vertical line Y4) and the carrier Cr (vertical line Y3) and the distance between the carrier Cr (vertical line Y3) and the ring gear Rr (vertical line Y2) is the gear of the third planetary gear 6. The ratio is set to k: 1, where k is the ratio.
  Here, in the first embodiment, the ring gear Rf (second element) of the first planetary gear 4, the carrier Cm (fifth element) of the second planetary gear 6, and the ring gear Rr (seventh element) of the third planetary gear 7 are coupled. The first coupling bodies Rf, Cm, Rr (vertical line Y2) are configured, the input shaft 2 is coupled to the carrier Cf (third element) of the first planetary gear 4, and the ring gear Rm (sixth sixth) of the second planetary gear 6 is coupled. Element) and the sun gear Sr (the ninth element) of the third planetary gear 7 are connected to form the second connecting body Rm, Sr, and the carrier Cr (the eighth element) of the third planetary gear 7 is the output member 3 serving as an output member. It is linked to.
  Further, as an engagement element, a first clutch C1 as a first engagement element that can be switched between a state in which the sun gear Sm (fourth element) of the second planetary gear 6 and the input shaft 2 are connected and a state in which the connection is cut off. The second clutch C2, which is a second engagement element that can be switched between a state in which the second connecting bodies Rm, Sr and the input shaft 2 are connected via the carrier Cf and a state in which the connection is cut off, and a second planetary gear 6 A first brake B1, which is a third engagement element that can be switched between a state in which the sun gear Sm (fourth element) is fixed to the transmission case 1 and a state in which the sun gear Sm is released, and a first coupling body Rf, Cm, Rr. A state in which the second brake B2, which is a fourth engagement element that can be switched between a state in which the transmission case 1 is fixed and a state in which the fixation is released, and a state in which the second coupling bodies Rm, Sr are fixed to the transmission case 1 It can be switched to the state of releasing the fixation. The fifth brake B3, which is the fifth engagement element, and the sixth engagement element, which is switchable between a state in which the sun gear Sf (first element) of the first planetary gear is fixed to the transmission case 1 and a state in which the fixation is released. 4 brakes B4.
  When the first clutch C1 and the third brake B3 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "1", the ring gear Rm of the second planetary gear 6, the third planetary gear 7 The rotational speed at the vertical line Y4 where the sun gear Sr is located is “0”, and the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 connected to the output gear 3 is located is “1st”. 1st gear is established.
  When the third brake B3 and the fourth brake B4 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 4 and the sun gear Sr of the third planetary gear is “0”, and the rotational speed of the carrier Cf of the first planetary gear 4 is “ 1 ”, the rotation speed of the ring gear Rf of the first planetary gear 4 and the rotation speed of the ring gear Rr (vertical line Y2) of the third planetary gear 7 become N1 ((i−1) / i), and the third planetary gear 7 The rotational speed at the vertical line Y3 where the second carrier Cr is located is “2nd”, and the second speed stage is established.
  When the first clutch C1 and the fourth brake B4 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "1", the ring gear Rf of the first planetary gear 4, the second planetary gear 6 The rotational speed at the vertical line Y2 at which the carrier Cm of the third planetary gear 7 is located and the vertical line Y2 at which the ring gear Rr of the third planetary gear 7 is located is N1, and the rotational speed at the vertical line Y3 at which the carrier Cr of the third planetary gear 7 is located is 3rd. A speed is established.
  When the first brake B1 and the fourth brake B4 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is “0”, the ring gear Rf of the first planetary gear 4 and the second planetary gear 6 The rotational speed at the vertical line Y2 where the carrier Cm and the ring gear Rr of the third planetary gear 7 are located is N1, and the rotational speed at the vertical line Y3 where the carrier Cr is located at the third planetary gear 7 is "4th". A speed is established.
  When the second clutch C2 and the fourth brake B4 are engaged, the rotational speed of the third planetary gear 7 at the vertical line Y5 where the sun gear Sr is located is "1", the ring gear Rf of the first planetary gear 4, the third planetary gear 7 The rotational speed at the vertical line Y2 where the ring gear Rr is located is N1, the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is "5th", and the fifth gear is established.
  When the second clutch C2 and the first brake B1 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "0", the ring gear Rm of the second planetary gear 6, the third planetary gear 7 The rotational speed at the vertical line Y4 where the sun gear Sr is located is "1", the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is "6th", and the sixth gear is established. .
  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed at the vertical line Y1 where the sun gear Sm of the second planetary gear 6 is located and the vertical line Y5 where the ring gear Rm of the second planetary gear 6 is located is “1”. The elements of the second planetary gear 6 are in a locked state in which relative rotation is impossible. As a result, the third planetary gear 7 is also locked, the rotational speed of the third planetary gear 7 along the vertical line Y3 where the carrier Cr is located is also “1”, “7th”, and the seventh gear is established.
  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is "1", the carrier Cm of the second planetary gear 6 and the third planetary gear 7 The rotational speed at the vertical line Y2 where the ring gear Rr is located is “0”, the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is negative “Rev”, and the reverse gear is established. Is done.
  FIG. 1B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1 and C2 and the brakes B1, B2, B3, and B4. “O” represents engagement. ing. FIG. 1B shows each of the cases where the gear ratio i of the first planetary gear 4 is 2.0, the gear ratio of the second planetary gear 6 is 2.7, and the gear ratio of the third planetary gear 7 is 1.5. The gear ratio of the shift speed (the rotational speed of the input shaft 2 / the rotational speed of the output gear 3) is also shown. According to this, the common ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (ratio of the first gear ratio to the seventh gear ratio (the first gear stage in FIG. 1B) Appears in the column to the right of the gear ratio))).
  According to the first embodiment, seven forward shifts can be performed by the two clutches C1, C2 and the four brakes B1, B2, B3, B4. In addition, the first brake B1 is disposed radially outward of the first clutch C1, the second brake B2 is disposed radially outward of the compound planetary gear 5, and the third brake B3 is radially outward of the second clutch C2. Can be arranged in the direction. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the axial length of the automatic transmission can be shortened by disposing the brake radially outside the clutch or the planetary gear.
  Next, an automatic transmission according to a second embodiment of the present invention will be described with reference to FIGS. In the transmission case 1 of the second embodiment, a first planetary gear 4 for input and a double planetary gear 5 for shifting are arranged around the input shaft 2. The first planetary gear 4 is a double-pinion type single planetary gear, as in the first embodiment.
  Referring to the velocity diagram of the first planetary gear 4 shown in the upper part of FIG. 4, three elements including the sun gear Sf, the carrier Cf, and the ring gear Rf of the first planetary gear 4 are arranged at intervals corresponding to the gear ratio in the velocity diagram. If the first element, the second element, and the third element are arranged from the left side in the order in which they are arranged, the first element is the carrier Cf, the second element is the ring gear Rf, and the third element is the sun gear Sf. The ratio between the distance between the sun gear Sf and the carrier Cf and the distance between the carrier Cf and the ring gear Rf is set to i: 1 where i is the gear ratio of the first planetary gear 4.
  In the second embodiment, the carrier Cf (first element) is fixed to the transmission case 1 as a fixed element, the ring gear Rf (second element) is connected to the input shaft 2 as an input element, and the sun gear Sf ( The third element) is the output element. The output speed of the first planetary gear 4 (the rotational speed of the sun gear Sf) N1 is “i”. 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 embodiment, the double planetary gear 5 of the second embodiment is composed of second and third planetary gears 6 and 7 of a single pinion type. Referring to the speed diagram of the double planetary gear 5 shown in the lower part of FIG. 4, the three elements including the sun gear Sm, the carrier Cm, and the ring gear Rm of the second planetary gear 6 are arranged at intervals corresponding to the gear ratio in the speed diagram. The fourth element is the sun gear Sm, the fifth element is the carrier Cm, and the sixth element is the ring gear Rm. The ratio between the distance between the sun gear Sm and the carrier Cm and the distance between the carrier Cm and the ring gear Rm is set to j: 1 where j is the gear ratio of the second planetary gear 6.
  Further, referring to the velocity diagram of the compound planetary gear 5, the three elements including the sun gear Sr, the carrier Cr and the ring gear Rr of the third planetary gear 7 are arranged in the order corresponding to the gear ratio in the velocity diagram. Assuming that the seventh element, the eighth element, and the ninth element are the left side, the seventh element is the ring gear Rr, the eighth element is the carrier Cr, and the ninth element is the sun gear Sr. The ratio between the distance between the sun gear Sr (vertical line Y4) and the carrier Cr (vertical line Y3) and the distance between the carrier Cr (vertical line Y3) and the ring gear Rr (vertical line Y2) is the gear of the third planetary gear 6. The ratio is set to k: 1, where k is the ratio.
  Here, in 2nd Embodiment, the carrier Cm (5th element) of the 2nd planetary gear 6 and the ring gear Rr (7th element) of the 3rd planetary gear 7 are connected, and 1st connection body Cm, Rr (vertical line Y2) is connected. ), The input shaft 2 is connected to the ring gear Rf (second element) of the first planetary gear 4, and the ring gear Rm (sixth element) of the second planetary gear 6 and the sun gear Sr (ninth element) of the third planetary gear 7. Are connected to each other to form a second connecting body Rm, Sr, and the carrier Cr (eighth element) of the third planetary gear 7 is connected to the output gear 3 as an output member.
  In addition, as an engagement element, a first gear that can be switched between a state in which the sun gear Sf (third element) of the first planetary gear 4 and the sun gear Sm (fourth element) of the second planetary gear 6 are connected and a state in which the connection is cut off. Second engagement that can be switched between a state in which the first clutch C1, which is an engagement element, the sun gear Sf (third element) of the first planetary gear 4 and the second coupling bodies Rm, Sr are coupled, and a state in which the coupling is disconnected. A second clutch C2, which is an element, a third clutch C3 which is a third engagement element which can be switched between a state where the input shaft 2 and the first connecting bodies Cm, Rr are connected and a state where the connection is disconnected, and a second planetary gear. The first brake B1 as a sixth engagement element that can be switched between a state in which the sun gear Sm (fourth element) 6 is fixed to the transmission case 1 via the carrier Cf of the first planetary gear 4 and a state in which the fixing is released. And first The second brake B2, which is a fourth engagement element that can be switched between a state in which the joints Cm, Rr are fixed to the transmission case 1 and a state in which the fixation is released, and the second coupling bodies Rm, Sr are connected to the transmission case 1. And a third brake B3 that is a fifth engagement element that can be switched between a state of being fixed to the state of releasing the fixed state and a state of releasing the fixing.
  When the first clutch C1 and the third brake B3 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is N1, and the vertical line Y4 at which the second coupling bodies Rm and Sr are located. Of the third planetary gear 7 connected to the output gear 3 at the vertical line Y3 where the carrier Cr is located is "1st", and the first gear is established.
  When the third clutch C3 and the third brake B3 are engaged, the rotational speed of the ring gear Rr (vertical line Y2) of the third planetary gear 7 constituting the first coupling bodies Cm, Rr is “1”, and the second coupling body. The rotational speed of the sun gear Sr (vertical line Y4) of the third planetary gear 7 constituting Rm, Sr is “0”, and the rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is “2nd”. Thus, the second gear is established.
  When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is N1, and the second planetary gear 6 constituting the first coupling bodies Cm, Rr. The rotational speed of the carrier Cm, the ring gear Rr (vertical line Y2) of the third planetary gear 7 is "1", the rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is "3rd", Third gear is established.
  When the third clutch C3 and the first brake B1 are engaged, the rotational speed at the vertical line Y1 where the sun gear Sm of the second planetary gear 6 is located is “0”, and the vertical line where the first coupling bodies Cm and Rr are located. The rotational speed at Y2 is “1”, the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is “4th”, and the fourth speed stage is established.
  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed at the vertical line Y4 where the sun gear Sr of the third planetary gear 7 is located is N1, and the vertical line Y2 at which the ring gear Rr of the third planetary gear 7 is located. The rotation speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is "5th", and the fifth gear is established.
  When the second clutch C2 and the first brake B1 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is “0”, and the second connecting members Rm and Sr are configured. The rotational speed at the vertical line Y4 where the ring gear Rm of the planetary gear 6 and the sun gear Sr of the third planetary gear 7 are located is N1, and the rotational speed at the vertical line Y3 where the carrier Cr of the third planetary gear 7 is located is "6th". 6th gear is established.
  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed at the vertical line Y1 where the sun gear Sm of the second planetary gear 6 is located and the vertical line Y4 where the ring gear Rm of the second planetary gear 6 is located is N1. Thus, each element of the second planetary gear 6 is in a locked state where relative rotation is impossible. Along with this, the third planetary gear 7 is also locked, the rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located is also “7th”, which is N1, and the seventh gear is established.
  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the second planetary gear 6 at the vertical line Y1 where the sun gear Sm is located is N1, and the vertical line Y2 at which the first coupling bodies Cm and Rr are located. The rotational speed of the third planetary gear 7 at the vertical line Y3 where the carrier Cr is located becomes negative “Rev”, and the reverse speed is established.
  FIG. 3B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, and C3 and the brakes B1, B2, and B3. “O” represents engagement. ing. FIG. 3B shows each of the cases where the gear ratio i of the first planetary gear 4 is 2.0, the gear ratio of the second planetary gear 6 is 2.7, and the gear ratio of the third planetary gear 7 is 1.5. The gear ratio of the shift speed (the rotational speed of the input shaft 2 / the rotational speed of the output gear 3) is also shown. According to this, the common ratio (the ratio of the gear ratio between the respective gears) becomes appropriate, and the ratio orange (the ratio of the gear ratio of the first speed to the gear ratio of the seventh speed (the first gear stage of FIG. 3B) Appears in the column to the right of the gear ratio))).
  According to the automatic transmission of the second embodiment, it is possible to perform a forward seven-speed shift with three clutches and three brakes. Further, the second brake B2 as the fourth engagement element is disposed radially outward of the double planetary gear 5, and the third brake B3 as the fifth engagement element is radially outward of the second clutch C2 as the second engagement element. Can be arranged in the direction. Accordingly, the number of clutches can be reduced as compared with the conventional one, and the brake can be disposed radially outward of the clutch or the planetary gear, so that the axial length of the automatic transmission can be shortened.
  In addition, like the automatic transmission of the third embodiment shown in FIG. 5, the third planetary gear 7 of the first embodiment is arranged on the radially outer side of the second planetary gear 6, and the ring gear Rm of the second planetary gear 6 and the third planetary gear are arranged. 7 sun gear Sr may be integrally formed. According to this, the shaft length of the transmission can be further shortened. Similarly, in the second embodiment, the third planetary gear 7 can be disposed radially outside the second planetary gear 6 to shorten the axial length.
  Further, as in the automatic transmission of the fourth embodiment shown in FIG. 6, instead of the multi-plate clutch type second brake B2 as the fourth engagement element of the first embodiment, the first coupling bodies Rf, Cm, Rr A dog clutch D1 that can be switched between a state in which the gear is fixed to the transmission case 1 and a state in which the fixing is released may be used. As a result, the friction loss associated with the release of the multi-plate clutch at the forward stage can be reduced and the transmission efficiency can be improved as compared with the multi-plate clutch. The dog clutch D1 includes a movable dog D1a splined to the outer periphery of the ring gear Rr of the third planetary gear 7, and a fixed dog D1b fixed in the transmission case 1. The dog teeth of the movable dog D1a are connected to the dog teeth of the fixed dog D1b. Engagement with the dog teeth restrains the rotation of the ring gear Rr. Similarly, the second brake B2 as the fourth engagement element of the second embodiment and the second brake B2 of the third embodiment are replaced with dog clutches, so that friction loss due to the release of the multi-plate clutch at the forward gear is reduced. It is possible to reduce the transmission efficiency.
(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. The speed diagram of the 1st-3rd planetary gear of 1st Embodiment. (A) is a skeleton figure of 2nd Embodiment of the automatic transmission of this invention, (b) is a figure which shows collectively the relationship between each gear stage and the engagement state of each engagement element. The speed diagram of the 1st-3rd planetary gear of 2nd Embodiment. The skeleton figure of 3rd Embodiment of the automatic transmission of this invention. The skeleton figure of 4th Embodiment of the automatic transmission of this invention.
Explanation of symbols
DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output gear, 4 ... 1st planetary gear, 5 ... Double planetary gear, 6 ... 2nd planetary gear, 7 ... 3rd planetary gear, Sf ... Sun gear of 1st planetary gear (1st element) ), Rf: ring gear (second element) of the first planetary gear, Cf: carrier of the first planetary gear (third element), Sm: sun gear (fourth element) of the second planetary gear, Rm: ring gear (second element) of the second planetary gear 6 element), Cm: second planetary gear carrier (fifth element), Sr ... third planetary gear sun gear (ninth element), Rr ... third planetary gear ring gear (seventh element), Cr ... third planetary gear carrier (8th element), C1 ... 1st clutch (1st engagement element), C2 ... 2nd clutch (2nd engagement element), C3 ... 3rd clutch (3rd engagement element of 2nd Embodiment), B1 ... 1st brake (3rd engagement element of 1st, 3rd, 4th embodiment, 6th engagement element of 2nd Embodiment), B2 ... 2nd Brake (fourth engagement element), B3 ... third brake (fifth engagement element), B4 ... fourth brake (sixth engagement element), D1 ... DOG clutch.

Claims (4)

  1. An automatic transmission that shifts the rotation of an input member to a plurality of stages through a first planetary gear for input disposed in a transmission case and a dual planetary gear for transmission and transmits it to an output member.
    The compound planetary gear is composed of the second and third planetary gears,
    The three elements including the sun gear, the carrier, and the ring gear of the first planetary gear are set as the first element, the second element, and the third element in the order corresponding to the gear ratio in the velocity diagram, respectively. The sun gear of the second planetary gear The three elements consisting of the carrier and the ring gear are designated as the fourth element, the fifth element, and the sixth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, and from the sun gear, the carrier, and the ring gear of the third planetary gear. The three elements consisting of the seventh element, the eighth element, and the ninth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
    The first element is configured by connecting the second element, the fifth element, and the seventh element, the input member is connected to the third element, and the second element is connected by connecting the sixth element and the ninth element. And the eighth element is connected to the output member,
    A first engagement element switchable between a state in which the fourth element and the input member are connected and a state in which the connection is broken;
    A second engagement element that is switchable between a state in which the second connection body and the input member are connected and a state in which the connection is broken;
    A three-engagement element switchable between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released;
    A fourth engagement element switchable between a state in which the first coupling body is fixed to the transmission case and a state in which the fixation is released;
    A fifth engagement element switchable between a state in which the second coupling body is fixed to the transmission case and a state in which the fixation is released;
    An automatic transmission comprising: a sixth engaging element that is switchable between a state in which the first element is fixed to the transmission case and a state in which the fixing is released.
  2. An automatic transmission that shifts the rotation of an input member to a plurality of stages through a first planetary gear for input disposed in a transmission case and a dual planetary gear for transmission and transmits it to an output member.
    The compound planetary gear is composed of the second and third planetary gears,
    The three elements including the sun gear, the carrier, and the ring gear of the first planetary gear are set as the first element, the second element, and the third element in the order corresponding to the gear ratio in the velocity diagram, respectively. The sun gear of the second planetary gear The three elements consisting of the carrier and the ring gear are designated as the fourth element, the fifth element, and the sixth element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, and from the sun gear, the carrier, and the ring gear of the third planetary gear. The three elements consisting of the seventh element, the eighth element, and the ninth element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram,
    The first element is fixed to the transmission case, the input member is connected to the second element, the fifth element and the seventh element are connected to form a first connection body, and the sixth element and the ninth element are connected. The second connected body is configured by connecting, and the eighth element is connected to the output member,
    A first engagement element that is switchable between a state in which the third element and the fourth element are connected and a state in which the connection is cut off;
    A second engagement element that is switchable between a state in which the third element and the second connection body are connected and a state in which the connection is broken;
    A third engagement element switchable between a state in which the first connection body and the input member are connected and a state in which the connection is cut off;
    A fourth engagement element switchable between a state in which the first coupling body is fixed to the transmission case and a state in which the fixation is released;
    A fifth engagement element switchable between a state in which the second coupling body is fixed to the transmission case and a state in which the fixation is released;
    An automatic transmission comprising a sixth engaging element that is switchable between a state in which the fourth element is fixed to the transmission case and a state in which the fixation is released.
  3. The automatic transmission according to claim 1 or 2,
    The sixth element is a ring gear of the second planetary gear, the ninth element is a sun gear of the third planetary gear, the third planetary gear is disposed radially outside the second planetary gear, and the ring gear of the second planetary gear and the sun gear of the third planetary gear And an integrated transmission to form a second coupling body.
  4.   The automatic transmission according to any one of claims 1 to 3, wherein the fourth engagement element is a dog clutch.
JP2008272912A 2008-10-23 2008-10-23 Automatic transmission Pending JP2010101404A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008272912A JP2010101404A (en) 2008-10-23 2008-10-23 Automatic transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008272912A JP2010101404A (en) 2008-10-23 2008-10-23 Automatic transmission

Publications (1)

Publication Number Publication Date
JP2010101404A true JP2010101404A (en) 2010-05-06

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Application Number Title Priority Date Filing Date
JP2008272912A Pending JP2010101404A (en) 2008-10-23 2008-10-23 Automatic transmission

Country Status (1)

Country Link
JP (1) JP2010101404A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012207017A1 (en) * 2012-04-27 2013-10-31 Zf Friedrichshafen Ag Multi-speed transmission
DE102019218627A1 (en) * 2019-11-29 2021-06-02 Volkswagen Aktiengesellschaft Augmented reality head-up display

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012207017A1 (en) * 2012-04-27 2013-10-31 Zf Friedrichshafen Ag Multi-speed transmission
US9080648B2 (en) 2012-04-27 2015-07-14 Zf Friedrichshafen Ag Multi-stage transmission
DE102019218627A1 (en) * 2019-11-29 2021-06-02 Volkswagen Aktiengesellschaft Augmented reality head-up display

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