JP2010060096A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission excelling in meshed transmission efficiency and improved in total transmission efficiency of all shift stages. <P>SOLUTION: This automatic transmission is provided with first-third planetary gears 5, 6 and 7. First connected bodies Rf and Cm are constituted by connecting a ring gear Rf of the first planetary gear 5 and a carrier Cm of the second planetary gear 6, and second connected bodies Sm and Rr are constituted by connecting a sun gear Sm of the second planetary gear and a ring gear Rr of the third planetary gear 7. A carrier Cf is connected to an output shaft 3 through a first gear row G1, and a ring gear Rm is connected through a second gear row G2. The automatic transmission is provided with a first engagement element C1 for connecting a sun gear Sf and an input shaft 2, a second engagement element C2 for connecting the first connectied bodies Rf and Cm and the input shaft 2, a third engagement element B1 for fixing the first connected bodies Rf and Cm to a case, a fourth engagement element B2 for fixing a sun gear Sr to the case, and a fifth engagement element B3 for fixing the second connected bodies Sm and Rr to the case. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an automatic transmission in which the rotation of an input shaft is shifted to a plurality of stages through a plurality of planetary gears arranged concentrically with the input shaft and transmitted to an output member.

  Conventionally, as an automatic transmission of this type, according to Patent Document 1, three forward planetary gears and five engaging elements arranged concentrically with an input shaft are used, and six forward stages are used. What performs a shift is known. In this device, the first planetary gear and the second planetary gear are of a single pinion type, the third planetary gear is of a double pinion type, and the sun gear of the first planetary gear is connected to the input shaft.

  The ring gears of the second planetary gear and the third planetary gear are formed of the same member, and the pinion supported by the carrier of the second planetary gear is one of the pair of pinions of the third planetary gear, and the carrier of the second planetary gear and the third planetary gear are used. And the second and third planetary gears constitute a double planetary gear. The compound planetary gear includes a first rotating element composed of a sun gear of a third planetary gear, a second rotating element composed of a ring gear of a second planetary gear shared with a ring gear of a third planetary gear, a carrier of a second planetary gear, and a carrier of a third planetary gear. And a fourth rotating element composed of a sun gear of the second planetary gear. These first to fourth rotating elements are arranged in order at intervals corresponding to the gear ratio in the velocity diagram. The first rotating element is connected to the carrier of the first planetary gear, and 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 fourth rotation element and the input shaft are connected and a state in which the connection is cut off, a state in which the second rotation element and the input shaft are connected, and this connection A second clutch which can be switched to a state where the first rotation element is cut off, a first brake which can be switched between a state where the first rotating element is fixed to the transmission case and a state where the fixing is released, and a second rotating element which is switched to the transmission case A second brake that can be switched between a state of being fixed to the state and a state of releasing the fixing, a third brake that is switchable between a state of fixing the ring gear of the first planetary gear to the transmission case and a state of releasing the fixing. It has.

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 clutch and the third brake, the fourth speed is established by engaging the first clutch and the second clutch, and the second clutch and the third brake are engaged. The fifth gear is established by engaging, and the sixth gear is established by engaging the second clutch and the first brake.
Japanese Patent Laying-Open No. 2003-240068 (FIG. 4)

  The mesh transmission efficiency of the conventional example is 97.8% at the first speed stage, 97.9% at the second speed stage, 98.1% at the third speed stage, 100% at the fourth speed stage, and 97 at the fifth speed stage. 7%, 97.0% for 6th gear, and 98.1% for forward gear.

  An object of the present invention is to provide an automatic transmission with better transmission efficiency than in the past.

  In order to achieve the above object, the present invention provides an automatic transmission that shifts the rotation of an input shaft to a plurality of stages via a plurality of planetary gears arranged concentrically with the input shaft and transmits the transmission to an output member. , The second planetary gear and the third planetary gear, and the three elements including the sun gear, the carrier and the ring gear of the first planetary gear are arranged in the order corresponding to the gear ratio in the speed diagram in the order of arrangement, respectively. The fourth element, the fifth element, and the sixth element are arranged in the order corresponding to the gear ratio in the speed diagram, and the three elements including the sun gear, the carrier, and the ring gear of the second planetary gear. And the three elements comprising the sun gear, the carrier, and the ring gear of the third planetary gear are arranged in the order corresponding to the gear ratio in the speed diagram. As the 7th element, the 8th element, and the 9th element, the 3rd element and the 5th element are connected to form the first connection body, and the 4th element and the 8th element are connected to form the 2nd connection body. The ninth element is connected to the input shaft, the second element is connected to the output shaft, which is an output member arranged parallel to the input shaft, via the first gear train, and the sixth element is connected to the first gear train. A first engagement element that is connected via a second gear train having a gear ratio different from that of the first engagement element and is switchable between a state in which the first element and the input shaft are connected to each other and a state in which the connection is cut off; A second engagement element that can be switched between a state in which the input shaft is connected and a state in which the connection is cut off, and a second engagement element that is switchable between a state in which the first connecting body is fixed to the transmission case and a state in which the fixing is released. A fourth engagement switchable between a state in which the three engagement elements and the seventh element are fixed to the transmission case and a state in which the fixation is released And iodine, characterized in that it comprises a fifth engagement element freely switched to a state of releasing the fixed state of fixing the second connecting member to the transmission case.

  According to the present invention, as will be apparent from the description of the embodiment to be described later, it is possible to perform forward six speeds and greatly improve the transmission efficiency on the high speed side such as the fifth speed and the sixth speed. , The total transmission efficiency of all gears is improved.

  Further, in the present invention, if a sixth engagement element that can be switched between a state in which the second connecting body and the input shaft are connected and a state in which the connection is cut off is provided, a forward eight-speed shift can be performed. And the first planetary gear in two speed stages, that is, a speed stage that engages the first engagement element and the second engagement element and a speed stage that engages the second engagement element and the sixth engagement element. Or since the 2nd planetary gear will be in a locked state, meshing transmission efficiency will be 100% and the total transmission efficiency of all the gear stages will improve.

  In the present invention, one of the first planetary gear and the third planetary gear and the second planetary gear are configured by a single pinion type planetary gear, and the other of the first planetary gear and the third planetary gear is configured by a double pinion type planetary gear. Alternatively, all of the first to third planetary gears may be constituted by a single pinion type planetary gear. Since the number of meshing can be reduced by using a single pinion type planetary gear, transmission efficiency can be further improved.

  Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. The first embodiment includes an input shaft 2 that is rotatably supported in a transmission case 1 and connected to a power source such as an engine (not shown), and an output shaft that is an output member arranged in parallel with the input shaft 2. 3 is provided. The rotation of the output shaft 3 is transmitted to the left and right drive wheels of the vehicle via a differential gear 4 in which a final driven gear 4a meshing with an output gear 3a fixed to the output shaft 3 is fixed.

  In the transmission case 1, a first planetary gear 5, a second planetary gear 6, and a third planetary gear 7 are disposed concentrically with the input shaft 2. The first planetary gear 5 is constituted by a single pinion type planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the sun gear Sf and the ring gear Rf so as to freely rotate and revolve.

  With reference to a speed diagram of the first planetary gear 5 shown in the lower part of FIG. 2 (a diagram in which the rotational speeds of the three elements of the sun gear, the carrier, and the ring gear can be represented by straight lines), the sun gear Sf of the first planetary gear 5 Assuming that the three elements comprising the carrier Cf and the ring gear Rf are the first element, the second element, and the third element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, respectively, the first element is the sun gear Sf. The second element is the carrier Cf, and the third element is the ring gear Rf. Here, 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 i: 1 where the gear ratio of the first planetary gear 5 (number of teeth of the ring gear / number of teeth of the sun gear) is i. Set to 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 5, the second planetary gear 6 is a single pinion type comprising a sun gear Sm, a ring gear Rm, and a carrier Cm that supports the sun gear Sm and the ring gear Rm so as to rotate and revolve. It is composed of planetary gears.

  Referring to the speed diagram of the second planetary gear 6 shown in the middle stage of FIG. 2, 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. If the fourth element, the fifth element, and the sixth element are respectively arranged from the left side in the order of arrangement, 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.

  The third planetary gear 7 includes a sun gear Sr, a ring gear Rr, and a carrier Cr that supports a pair of pinions Pr and Pr ′ that are meshed with each other and one meshed with the sun gear Sr and the other meshed with the ring gear Rr. It is composed of a double pinion type planetary gear.

  Referring to the speed diagram of the third planetary gear 7 shown in the upper part of FIG. 2, three elements including the sun gear Sr, the carrier Cr, and the ring gear Rr of the third planetary gear 7 are separated by a distance corresponding to the gear ratio in the speed diagram. If the seventh element, the eighth element, and the ninth element are respectively arranged from the left side in the order in which they are arranged, the seventh element is the sun gear Sr, the eighth element is the ring gear Rr, and the ninth element is the carrier Cr. The ratio between the distance between the sun gear Sr and the carrier Cr and the distance between the carrier Cr and the ring gear Rr is set to k: 1 where k is the gear ratio of the third planetary gear 7.

  The ring gear Rf (third element) of the first planetary gear 5 and the carrier Cm (fifth element) of the second planetary gear 6 are connected to each other to form first connected bodies Rf and Cm. The sun gear Sm (fourth element) of the second planetary gear 6 and the ring gear Rr (eighth element) of the third planetary gear 7 are connected to each other to form second connected bodies Sm, Rr. A carrier Cr (9th element) of the third planetary gear 7 is connected to the input shaft 2. The carrier Cf (second element) of the first planetary gear 5 has a first gear train G1 including a drive gear G1a fixed to the carrier Cf and a driven gear G1b fixed to the output shaft 3 meshing with the drive gear G1a. The ring gear Rm (sixth element) of the second planetary gear 6 is connected to the output shaft 3 through a drive gear G2a fixed to the ring gear Rm and a driven gear G2b fixed to the output shaft 3 meshing with the drive gear G2a. It is connected to the output shaft 3 via the second gear train G2.

  Here, p> q, where p is the gear ratio of the first gear train G1 (number of teeth of the driven gear / number of teeth of the drive gear) and q is the gear ratio of the second gear train G2. Further, the carrier Cf of the first planetary gear 5 and the ring gear Rm of the second planetary gear 6 are coupled by the output shaft 3 via both gear trains G1 and G2. The ring gear Rm of the second planetary gear 6 rotates at a speed q / p of the rotation speed of the carrier Cf of the first planetary gear 5.

  In the first embodiment, as the engagement element, a first engagement element that can be switched between a state in which the sun gear Sf (first element) of the first planetary gear 5 and the input shaft 2 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 first clutch C1, the first coupling bodies Rf, Cm (third element, fifth element) and the input shaft 2 are coupled and a state in which the coupling is disconnected. A first engagement element that is switchable between a state in which the two-clutch C2 and the first coupling bodies Rf, Cm (third element, fifth element) are fixed to the transmission case 1 and a state in which the fixing is released is possible. A brake B1, a second brake B2 as a fourth engagement element which can be switched between a state in which the sun gear Sr (seventh element) of the third planetary gear 7 is fixed to the transmission case 1 and a state in which the fixation is released; Two transmissions Sm, Rr (fourth element, eighth element) transmission And a third brake B3 serving capable of switching a fifth engagement element to a state of fixing the over scan 1 and a state of releasing the fixing. The transmission case 1 is connected in parallel with the first brake B1 to a one-way clutch F1 that allows normal rotation (rotation in the forward direction) of the first coupling bodies Rf and Cm and prevents reverse rotation. .

  In the first embodiment, when the first clutch C1 is engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is “1”, and the rotational speed of the ring gear Rf of the first planetary gear 5 is the function of the one-way clutch F1. The speed line of the first planetary gear 5 becomes a line indicated by “1st” in FIG. The rotation speed of the carrier Cf of the first planetary gear 5 is 1 / (i + 1), and the output shaft 3 rotates at a speed of 1 / {(i + 1) p} via the first gear train G1. A stage is established. When the first brake B1 is engaged in addition to the first clutch C1, the first gear is established with the engine brake being effective.

  When the first clutch C1 and the third brake B3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the sun gear Sm of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, and the ring gear Rm of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. The speed lines of the first planetary gear 5 and the second planetary gear 6 are the lines indicated by “2nd” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is (j + 1) p / {(i + 1) (j + 1) p-ijq}, and the rotational speed of the ring gear Rm of the second planetary gear 6 is (j + 1) q / {(i + 1). (J + 1) p−ijq}, and the output shaft 3 rotates at a speed of (j + 1) / {(i + 1) (j + 1) p−ijq} to establish the second gear.

  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the carrier Cr of the third planetary gear 7 both become “1”, and the third planetary gear 7 The rotation speed of the sun gear Sr becomes “0”, the ring gear Rf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, and the ring gear Rm of the second planetary gear 6 rotates in the first planetary gear 5. The speed line of the first planetary gear 5 and the second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf, and becomes a line indicated by “3rd” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is {k (j + 1) + i (k-1)} p / {(i + 1) (j + 1) kp-ijkq}, and the rotational speed of the ring gear Rr of the second planetary gear 6 is {K (j + 1) + i (k-1)} q / {(i + 1) (j + 1) kp-ijkq}, and the output shaft 3 becomes {k (j + 1) + i (k-1)} / {(i + 1) ( j + 1) kp−ijkq} and the third gear is established.

  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear. 5 is in a locked state, and the speed line of the first planetary gear 5 is a line indicated by “4th” in FIG. Then, the rotation speed of the carrier Cf of the first planetary gear 5 becomes “1”, the output shaft 3 rotates at a speed of 1 / p, and the fourth speed stage is established.

  When the second clutch C2 and the second brake B2 are engaged, the rotational speed of the carrier Cm of the second planetary gear 6 and the rotational speed of the carrier Cr of the third planetary gear 7 both become “1”, and the third planetary gear 7 The rotation speed of the sun gear Sr becomes “0”, the ring gear Rf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, and the ring gear Rm of the second planetary gear 6 rotates in the first planetary gear 5. The speed of the second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf, and becomes a line indicated by “5th” in FIG. Then, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes (1 + jk) / (jk), and the output shaft 3 rotates at a speed of (1 + jk) / (jkq) to establish the fifth gear.

  When the second clutch C2 and the third brake B3 are engaged, the rotation speed of the sun gear Sm of the second planetary gear 6 becomes “0”, the rotation speed of the carrier Cm of the second planetary gear 6 becomes “1”, and the second The speed line of the planetary gear 6 is a line indicated by “6th” in FIG. Then, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes (j + 1) / j, the output shaft 3 rotates at a speed of (j + 1) / (jq), and the sixth gear is established.

  When the first brake B1 and the second brake B2 are engaged, the rotational speed of the carrier Cm of the second planetary gear 6 and the rotational speed of the sun gear Sr of the third planetary gear 7 both become “0”, and the second planetary gear 6 The velocity line is a line indicated by “Rvs” in FIG. Then, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes − (k−1) / jk, the output shaft 3 rotates at a speed of − (k−1) / (jkq), and the reverse gear is established. The

  A speed line indicated by a dotted line in FIG. 2 represents that each element of the other planetary gear rotates following the planetary gear that transmits power among the first to third planetary gears 5, 6, and 7.

  FIG. 1 (b) is a diagram summarizing and displaying the relationship between the above-described shift speeds and the engagement states of the clutches C1, C2, the brakes B1, B2, B3, and the one-way clutch F1. Represents the event. 1B shows that the gear ratio i of the first planetary gear 5 is 2.65, the gear ratio j of the second planetary gear 6 is 1.85, the gear ratio k of the third planetary gear 7 is 3.00, The gear ratios (the rotational speed of the input shaft 2 / the rotational speed of the output shaft 3) when the gear ratio p of the gear train G1 is 1.10 and the gear ratio q of the second gear train G2 is 1.00. Show. According to this, the public ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (first speed ratio / 6 speed ratio) becomes appropriate.

  FIG. 3 shows the mesh transmission efficiency of each gear position according to the first embodiment. In FIG. 3, the mesh transmission efficiency (%) is shown in the left column of the column of the first embodiment, and the improvement over the conventional one is shown in the right column. When the meshing rate of each gear of the first embodiment is compared with the conventional one, as shown in the right column, the second gear is 0.3% lower, but the third gear and fifth gear, The efficiency at the 6th speed is greatly improved, and the average of the forward speed is improved by 0.57% from the conventional speed.

  In the first embodiment, the second clutch C2, the first clutch C1, the first planetary gear 5, the first gear train G1, and the second gear train G2 are sequentially arranged around the input shaft 2 from one end side. Although the second planetary gear 6 and the first brake B1, the one-way clutch F1, the third planetary gear 7, the third brake B3, and the second brake B2 are arranged, the present invention is not limited to this. For example, as in the second embodiment shown in FIG. 4, the first planetary gear and the first gear train G1 may be arranged between the first clutch C1 and the second gear train G2. Further, as in the third embodiment shown in FIG. 5, the first gear train G1, the first planetary gear 5, the first clutch C1, the second clutch C2, and the second gear are sequentially arranged from one end side of the input shaft 2. The row G2, the second planetary gear 6 and the first brake B1, the one-way clutch F1, the third planetary gear 7 and the third brake B3, and the second brake B2 may be arranged.

  In the first embodiment, each of the first and second planetary gears 5 and 6 is constituted by a single pinion type planetary gear, and the third planetary gear 7 is constituted by a double pinion type planetary gear. However, the double pinion type planetary gear is used. The first planetary gear 5 and the second planetary gear 6 may be configured, or the third planetary gear 7 may be configured by a single pinion type planetary gear. When the first planetary gear 5 is formed of a double pinion type planetary gear, one of the sun gear and the carrier is the first element, the ring gear is the second element, and the other of the sun gear and the carrier is the third element. When the second planetary gear 6 is constituted by a double pinion type planetary gear, one of the sun gear and the carrier is the fourth element, the ring gear is the fifth element, and the other of the sun gear and the carrier is the sixth element. Further, when the third planetary gear 7 is constituted by a single pinion type planetary gear, one of the sun gear and the ring gear is the seventh element, the carrier is the eighth element, and the other of the sun gear and the ring gear is the ninth element.

  When the third planetary gear 7 is constituted by a single pinion type planetary gear as in the fourth embodiment shown in FIG. 6, the number of meshes is reduced when the third planetary gear 7 is used for power transmission, so that the mesh transmission efficiency is further improved. Can be made. As shown in FIG. 7, in the fourth embodiment, the carrier Cr of the third planetary gear 7 is the eighth element, and the ring gear Rr is the ninth element. FIG. 6B shows the gear ratio (rotational speed / output shaft of the input shaft 2) when the gear ratio k of the third planetary gear 7 is 2.00 and other gear ratios are the same as those of the first embodiment. 3). According to this, the public ratio (ratio of gear ratios between the respective gears) becomes appropriate, and the ratio orange (first speed ratio / 6 speed ratio) becomes appropriate.

  FIG. 3 shows the mesh transmission efficiency of each gear position according to the fourth embodiment. Compared to the conventional one, the efficiency at the third speed, fifth speed, and sixth speed is greatly improved, but the average of the forward speed is 0.65% compared to the conventional speed although it is 0.3% lower at the second speed. It has improved.

  Moreover, you may comprise the 1st planetary gear 5 of 4th Embodiment by the double pinion type planetary gear like 5th Embodiment shown in FIG. Further, as in the sixth embodiment shown in FIG. 9, the third engagement can be switched between a state in which the first coupling bodies Cf and Cm of the fifth embodiment are fixed to the transmission case 1 and a state in which the fixing is released. The first brake B1 and the one-way clutch F1 as elements may be arranged at the positions of the first clutch C1 and the second clutch C2.

  Further, as in the seventh embodiment shown in FIG. 10, the first gear train G1 of the fourth embodiment is disposed between the first clutch C1 and the first planetary gear 5, and the first coupling bodies Rf, Cm are arranged in the transmission. The first brake B1 and the one-way clutch F1, which are third engagement elements that can be switched between a state of fixing to the case 1 and a state of releasing the fixing, may be disposed at the position of the first planetary gear 5. Further, as in the eighth embodiment shown in FIG. 11, it may be arranged between the first clutch C1, the second clutch C2, the first planetary gear 5, and the second gear train G2 of the seventh embodiment.

  Next, a ninth embodiment shown in FIG. In the ninth embodiment, a third clutch C3 as a sixth engagement element is added to the fourth embodiment. The third clutch C3 connects the input shaft 2 and the second connecting body Sm, Cr that connects the sun gear Sm that is the fourth element of the second planetary gear 6 and the carrier Cr that is the eighth element of the third planetary gear 7. It is configured to be switchable to a state where the connection is cut off. Other configurations are the same as those of the fourth embodiment.

  In this case, when the first clutch C1 is engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 is "1", and the rotational speed of the ring gear Rf of the first planetary gear 5 is "0" by the action of the one-way clutch F1. Thus, the speed line of the first planetary gear 5 becomes a line indicated by “1st” in FIG. The rotation speed of the carrier Cf of the first planetary gear 5 is 1 / (i + 1), and the output shaft 3 rotates at a speed of 1 / {(i + 1) p} via the first gear train G1. A stage is established. When the first brake B1 is engaged in addition to the first clutch C1, the first gear is established with the engine brake being effective.

  When the first clutch C1 and the third brake B3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 becomes “1”, the rotational speed of the sun gear Sm of the second planetary gear 6 becomes “0”, and The ring gear Rf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, and the ring gear Rm of the second planetary gear 6 rotates at the speed q / p of the rotational speed of the carrier Cf of the first planetary gear 5. The speed lines of the first planetary gear 5 and the second planetary gear 6 are indicated by “2nd” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is (j + 1) p / {(i + 1) (j + 1) p-ijq}, and the rotational speed of the ring gear Rm of the second planetary gear 6 is (j + 1) q / {(i + 1). (J + 1) p−ijq}, and the output shaft 3 rotates at a speed of (j + 1) / {(i + 1) (j + 1) p−ijq} to establish the second gear.

  When the first clutch C1 and the second brake B2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rr of the third planetary gear 7 both become “1”, and the third planetary gear 7 The rotation speed of the sun gear Sr becomes “0”, the ring gear Rf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, and the ring gear Rm of the second planetary gear 6 rotates in the first planetary gear 5. The speed line of the first planetary gear 5 and the second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf, and becomes a line indicated by “3rd” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is {k (j + 1) + i (k-1)} p / {(i + 1) (j + 1) kp-ijkq}, and the rotational speed of the ring gear Rr of the second planetary gear 6 is {K (j + 1) + i (k-1)} q / {(i + 1) (j + 1) kp-ijkq}, and the output shaft 3 becomes {k (j + 1) + i (k-1)} / {(i + 1) ( j + 1) kp−ijkq} and the third gear is established.

  When the first clutch C1 and the third clutch C3 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the sun gear Sm of the second planetary gear 6 both become “1”, and the first planetary gear. The ring gear Rf of No. 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, the ring gear Rm of the second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf of the first planetary gear 5, and The speed lines of the first planetary gear 5 and the second planetary gear 6 are indicated by “4th” in FIG. The rotational speed of the carrier Cf of the first planetary gear 5 is (i + j + 1) p / {(i + 1) (j + 1) p-ijq}, and the output shaft 3 is (i + j + 1) / {(i + 1) (j + 1) p-ijq. }, The fourth gear is established.

  When the first clutch C1 and the second clutch C2 are engaged, the rotational speed of the sun gear Sf of the first planetary gear 5 and the rotational speed of the ring gear Rf of the first planetary gear 5 both become “1”, and the first planetary gear. 5 is locked, and the speed line of the first planetary gear 5 is a line indicated by “5th” in FIG. Then, the rotation speed of the carrier Cf of the first planetary gear 5 becomes “1”, the output shaft 3 rotates at a speed of 1 / p, and the fifth speed stage is established.

  When the second clutch C2 and the third clutch C3 are engaged, the rotational speed of the sun gear Sm of the second planetary gear 6 and the rotational speed of the carrier Cm of the second planetary gear 6 both become “1”, and the second planetary gear. 6 is in a locked state, and the speed line of the second planetary gear 6 is a line indicated by “6th” in FIG. Then, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes “1”, the output shaft 3 rotates at a speed of 1 / q, and the sixth speed stage is established.

  When the second clutch C2 and the second brake B2 are engaged, the rotational speed of the carrier Cm of the second planetary gear 6 and the rotational speed of the ring gear Rr of the third planetary gear 7 both become “1”, and the third planetary gear 7 The rotation speed of the sun gear Sr becomes “0”, the ring gear Rf of the first planetary gear 5 and the carrier Cm of the second planetary gear 6 rotate at the same speed, and the ring gear Rm of the second planetary gear 6 rotates in the first planetary gear 5. The second planetary gear 6 rotates at the speed q / p of the rotation speed of the carrier Cf, and the speed line of the second planetary gear 6 becomes a line indicated by “7th” in FIG. The rotational speed of the ring gear Rm of the second planetary gear 6 is {j (k + 1) +1} / {j (k + 1)}, and the output shaft 3 is {j (k + 1) +1} / {j (k + 1) q}. Rotating at speed establishes 7th gear.

  When the second clutch C2 and the third brake B3 are engaged, the rotation speed of the sun gear Sm of the second planetary gear 6 becomes “0”, the rotation speed of the carrier Cm of the second planetary gear 6 becomes “1”, and the second The speed line of the planetary gear 6 is a line indicated by “8th” in FIG. Then, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes (j + 1) / j, the output shaft 3 rotates at a speed of (j + 1) / (jq), and the eighth gear is established.

  When the first brake B1 and the second brake B2 are engaged, the rotational speed of the carrier Cm of the second planetary gear 6 and the rotational speed of the sun gear Sr of the third planetary gear 7 both become “0”, and the second planetary gear 6 The speed line is a line indicated by “Rvs” in FIG. Then, the rotational speed of the ring gear Rm of the second planetary gear 6 becomes −k / {(k + 1) j}, and the output shaft 3 rotates at a speed of −k / {(k + 1) jq}, and the reverse gear is established. The

  FIG. 12 (b) is a diagram summarizing the relationship between the above-described shift speeds and the engagement states of the clutches C 1, C 2, C 3, the brakes B 1, B 2, B 3 and the one-way clutch F 1. Represents engagement. According to the ninth embodiment, a forward eight-stage transmission can be configured simply by providing the third clutch C3.

  In addition, also in the thing of 9th Embodiment, the arrangement position of each engagement element and each gear train can be changed.

  Moreover, although the said embodiment is an automatic transmission for FF vehicles, if a propeller shaft is connected with the output shaft 3, it can also be set as the automatic transmission for FR vehicles.

(A) Skeleton diagram of the first embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st-3rd planetary gear of 1st Embodiment. The table | surface which shows the meshing transmission efficiency of each gear stage of 1st Embodiment and 4th Embodiment. The skeleton figure of 2nd Embodiment of this invention transmission. The skeleton figure of 3rd Embodiment of this invention transmission. (A) Skeleton diagram of the fourth embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st-3rd planetary gear of 4th Embodiment. The skeleton figure of 5th Embodiment of this invention transmission. The skeleton figure of 6th Embodiment of this invention transmission. The skeleton figure of 7th Embodiment of this invention transmission. The skeleton figure of 8th Embodiment of this invention transmission. (A) Skeleton diagram of the ninth embodiment of the transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. The speed diagram of the 1st-3rd planetary gear of 9th Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft, 3 ... Output shaft, 5 ... 1st planetary gear, Sf ... Sun gear (1st element) of 1st planetary gear, Cf ... Carrier of 1st planetary gear (2nd element or 3rd element) ), Rf: Ring gear (third element or second element) of the first planetary gear, 6: Second planetary gear, Sm: Sun gear (fourth element) of the second planetary gear, Cm: Carrier of the second planetary gear (fifth element) , Rm ... second planetary gear ring gear (sixth element), 7 ... third planetary gear, Sr ... third planetary gear sun gear (seventh element), Cr ... third planetary gear carrier (ninth element or eighth element), Rm ... Ring gear (eighth element or ninth element) of the third planetary gear, G1 ... First gear train, G2 ... Second gear train, C1 ... First clutch (first engagement required) ), C2 ... second clutch (second engagement element), C3 ... third clutch (sixth engagement element), B1 ... first brake (third engagement element), B2 ... second brake (fourth engagement) Combination element), B3... Third brake (fifth engagement element).

Claims (4)

An automatic transmission that shifts the rotation of the input shaft to a plurality of stages via a plurality of planetary gears arranged concentrically with the input shaft, and transmits it to the output member,
A first planetary gear, a second planetary gear, and a third planetary gear;
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, and 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 third element and the fifth element are connected to form a first connecting body, the fourth element and the eighth element are connected to form a second connecting body, and the ninth element is connected to the input shaft. The second element is connected to the output shaft, which is an output member arranged in parallel with the input shaft, via the first gear train, and the sixth element is connected to the second gear train having a gear ratio different from that of the first gear train. Connected,
A first engagement element that is switchable between a state in which the first element and the input shaft are connected and a state in which the connection is broken;
A second engagement element switchable between a state of connecting the first connecting body and the input shaft and a state of disconnecting the connection;
A third 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 fourth engagement element switchable between a state in which the seventh element is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising: a fifth engagement element that is 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.   The automatic transmission according to claim 1, further comprising a sixth engagement element that is switchable between a state in which the second connecting body and the input shaft are connected and a state in which the connection is cut off.   One of the first planetary gear and the third planetary gear and the second planetary gear are configured by a single pinion type planetary gear, and the other of the first planetary gear and the third planetary gear is configured by a double pinion type planetary gear. The automatic transmission according to claim 1 or 2.   3. The automatic transmission according to claim 1, wherein each of the first to third planetary gears is a single pinion type planetary gear.

Images