JP2013160282A - Twin-clutch type transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission which reduces power loss due to co-rotation caused by a gear by simplifying a backing movement switching mechanism.SOLUTION: There is provided a twin-clutch type transmission 1 in which a torque of a power source is transmitted selectively to input shafts 2, 3 via a clutch and output shafts 10, 11 are arranged in parallel with the input shafts 2, 3 and then a couple of gears is provided between the output shafts 10, 11 and the input shafts 2, 3 and further a reverse gear is provided. In the twin-clutch type transmission 1, there is provided with a reverse drive gear engagement mechanism 17 for engaging a reverse drive gear15 and a second speed driven gear 13 with each other in a torque transmittable manner and a reverse driven gear mechanism 23 for coupling a reverse driven gear 22 and the output shaft 11 together in a torque transmittable manner. Further, an engagement mechanism 9 capable of selectively blocking out torque transmission is provided in mid-flow of a path for transmitting a torque, from a clutch for selectively coupling the input shafts 2, 3 transmitting power to the second speed driven gear 13, to the reverse drive gear engagement mechanism 17.

Description

  The present invention relates to a so-called twin latch type transmission having two clutch means for inputting power.

  This type of transmission is widely used as a transmission for a vehicle, and it is desired that the transmission for a vehicle is as small and light as possible and has many shift stages that can be set. Further, such a transmission is usually further provided with a reverse idler gear shaft for switching the vehicle from forward to reverse. However, as described above, since the transmission is desired to be smaller and lighter, this reverse idler is required. The gear shaft and the like need to be simplified. As an example, the double-clutch transmission described in Patent Document 1 has two input shafts and two output shafts, and a plurality of gear pairs for setting a gear position are arranged on each input shaft or on each input shaft. It is arranged on the output shaft and is configured to switch the gear pairs by a plurality of synchro mechanisms. In particular, the idler gear formed integrally with the driven gear for the second speed is coaxial with one of the output shafts. A reverse driven gear is provided on the same axis as the other output shaft so as to be rotatable. From an idler gear coupled to one output shaft by a synchro mechanism to another output shaft by another synchro mechanism. Power is transmitted to the coupled reverse driven gear to drive the vehicle backward.

  Further, the dual clutch automatic transmission described in Patent Document 2 includes a first input shaft and a second input shaft that are coaxially arranged, and a first output shaft and a second output that are arranged in parallel to the input shafts. A reverse gear is rotatably provided on the first output shaft, and the reverse gear is always meshed with the small-diameter gear so as to be freely rotatable on the second output shaft. Power is transmitted from a reverse gear coupled to the shaft to a small diameter gear coupled to the second output shaft by a shift clutch to cause the vehicle to travel backward.

  The dual clutch transmission described in Patent Document 3 arranges a plurality of gear pairs for setting a gear position on an input shaft, a sub shaft, or an output shaft, and transmits power by a plurality of clutches. In particular, the reverse gear supported rotatably on the countershaft is coupled to the countershaft by a clutch, so that the third gear supported on the output shaft from the reverse gear is configured. The vehicle is driven backward by transmitting power to the driven gear.

  Furthermore, the dual clutch transmission described in Patent Document 4 includes a first input shaft and a second input shaft that are coaxially arranged, and a first output shaft and a second output shaft that are arranged in parallel to the input shafts. And a plurality of gear pairs for setting a gear position are arranged on the input / output shafts, and a gear pair to which power is to be transmitted is switched by a plurality of clutches.

JP 2007-321819 A JP 2011-163458 A JP 2008-291893 A JP 2010-209951 A

  In the double clutch transmission described in Patent Document 1, a second-speed drive gear is integrally provided on one input shaft, and the second-speed drive gear is rotatably provided on a second output shaft. An idler gear is formed integrally with the second-speed driven gear. Therefore, when the second speed is selected in Patent Document 1, the second-speed drive gear rotates the idler gear together with the second-speed driven gear, and the reverse driven gear meshed with the idler gear. And the idler gear and the reverse driven gear are rotated together, and the power transmitted from the engine may be lost. Similarly, when the second speed is selected in Patent Document 2, the second-speed drive gear provided on the second input shaft has a small-diameter gear together with the second-speed driven gear meshing with the second-speed drive gear. The reverse gear meshed with the small-diameter gear is also rotated at the same time. As a result, the small-diameter gear and the reverse gear are rotated at the second speed, and the power transmitted from the engine may be lost. It was.

  The present invention has been made paying attention to the technical problems described above, and it is an object of the present invention to simplify a reverse switching mechanism and to provide a transmission with less power loss due to gear rotation. .

  In order to achieve the above object, according to the first aspect of the present invention, the first input shaft and the second input shaft to which power is selectively transmitted from the driving force source via the clutch are arranged on the same axis. In addition, a first output shaft and a second output shaft to which power is transmitted from these input shafts are arranged in parallel to each of the input shafts, and the first input shaft, the first output shaft, and the second output A plurality of pairs of gears having different gear ratios are provided between the first output shaft and the second output shaft, and between the second input shaft and the first output shaft and the second output shaft. In the twin clutch type transmission provided with a reverse gear pair for setting the reverse gear, the reverse drive gear constituting the reverse gear pair is disposed on one of the output shafts and the reverse thereof. Drive gear and one output A reverse drive engagement mechanism is provided for selectively connecting the upper gear to another gear so that torque can be transmitted, and a reverse driven gear constituting the reverse gear pair is disposed on one of the other output shafts. A reverse driven engagement mechanism that selectively connects the reverse driven gear and the other output shaft so as to be able to transmit torque, and outputs the power output from the driving force source to the other gear on the one output shaft. The transmission of torque can be selectively cut off in the path for transmitting torque from the clutch that selectively connects one of the input shafts to the drive force source to the reverse drive engagement mechanism. An engagement mechanism is provided.

  According to a second aspect of the present invention, in the first aspect of the invention, a further another gear that forms a pair with the other gear on the one output shaft can freely rotate to any one of the input shafts. The other engagement mechanism is provided on any one of the input shafts, and engages the further other gear and either one of the input shafts so that torque can be transmitted. A twin clutch transmission including a gear clutch.

According to a third aspect of the present invention, in the first or second aspect of the invention, the reverse driven gear is included in the plurality of pairs of gears rotatably provided on the other output shaft. The twin clutch is formed integrally, and the reverse driven gear engagement mechanism includes a shift stage clutch that engages the other output shaft and the other gear so that torque can be transmitted. Type transmission.

  Further, the invention according to claim 4 is the invention according to claim 1, wherein the plurality of pairs of gears are provided rotatably on the first speed drive gear provided on the first input shaft and on the other output shaft. A first-speed transmission gear pair including a first-speed driven gear, a second-speed driving gear provided on the second input shaft, and the other gear on the one output shaft. A third-speed transmission gear pair, a third-speed drive gear provided on the first input shaft, and a third-speed driven gear provided rotatably on the other output shaft. A fourth speed gear pair, a fourth speed driving gear rotatably provided on the second input shaft, and a fourth speed driven gear rotatably provided on the one output shaft. A first output shaft idle gear rotatably provided on the first speed drive gear and the first output shaft. A fifth speed transmission gear pair comprising an idle gear that constitutes the first gear, a second speed drive gear, and an idle gear constituting a second output shaft idle gear that is rotatably provided on the other output shaft. A sixth-speed transmission gear pair, a seventh-speed transmission gear pair comprising the third-speed drive gear, and another idle gear constituting the first output shaft idle gear, and the fourth-speed drive. An eighth-speed transmission gear pair including a gear and another idle gear constituting the second output shaft idle gear, and the first-speed drive gear or the third-speed drive gear and the first input. A first input shaft engaging mechanism that selectively couples a shaft so that torque can be transmitted, and the other gear on the one output shaft or the fourth driven gear and the second output shaft selectively. A first output shaft engaging mechanism coupled to transmit torque; It is a twin clutch type transmission, characterized in that e.

  According to the present invention, the engagement mechanism that engages the reverse drive gear so that torque can be transmitted is provided in the path between the clutch that enables transmission of torque transmitted from the power source and the reverse drive gear engagement mechanism. The reverse drive gear provided on the first output shaft meshes with the reverse driven gear provided on the second output shaft. By transmitting power from the reverse driver gear to the reverse driven gear, the rotation of the other output shaft is rotated in the reverse direction. Therefore, the reverse idler gear shaft for reverse driving is not required, the number of meshing gears is reduced, the power transmission efficiency is improved, and the transmission can be reduced in size and weight as much as possible.

  In the present invention, when the forward speed of the transmission is selected, the torque of the power source is input to the first or second input shaft via the clutch. However, when the path between the clutch and the reverse drive gear engagement mechanism and the reverse drive gear are not connected via the engagement mechanism, the torque input to the first or second input shaft is the reverse drive gear. Not transmitted to. Therefore, even if the reverse drive gear engagement mechanism is engaged with the reverse drive gear and the reverse drive gear and the reverse driven gear can transmit torque, the reverse drive gear and the reverse drive gear mesh with each other. Therefore, the power loss caused by the gear rotation can be reduced.

  In particular, according to the second aspect of the present invention, there is provided another gear which forms a pair with a gear on one output shaft and is rotatably supported on at least one of the first input shaft and the second input shaft. If the gear is not connected to the input shaft through the engagement mechanism, the torque transmitted from the power source to the input shaft through the clutch is not transmitted to the other gear. Rotation of the gear on one output shaft meshing with the gear does not occur, and power loss due to rotation of the gear can be reduced.

1 is a skeleton diagram showing a first embodiment of a dual clutch transmission according to the present invention. FIG. It is a skeleton figure which shows 2nd Example of the dual clutch type transmission which concerns on this invention. It is a skeleton figure which shows the reference example of the dual clutch type transmission which concerns on this invention. It is a skeleton which shows the other reference example of the dual clutch type transmission which concerns on this invention.

  The present invention will be described based on specific examples. FIG. 1 shows a dual clutch transmission of eight forward speeds and one reverse speed as a first embodiment of the transmission according to the present invention. First, the configuration will be described. The transmission 1 includes a first input shaft 2 and a second input shaft 3 that are rotating shafts that transmit torque transmitted from a power source (not shown). The first input shaft 2 and the second input shaft 3 are formed on the same axis, and transmit torque from a power source via first and second clutches (not shown). The first and second clutches are constituted by multi-plate clutches that selectively connect the first input shaft 2 or the second input shaft 3 and a power source. A first speed drive gear 4 and a third speed drive gear 5 are arranged on the shaft of the first input shaft 2 so as to be axially aligned and rotatable. Further, the first input shaft 2 includes a first-speed drive gear 4 or a third-speed drive gear 5 between the first-speed drive gear 4 and the third-speed drive gear 5 in the axial direction thereof. And a first input shaft engaging mechanism 6 for selectively connecting the first input shaft 2 and the first input shaft 2. The first input shaft engagement mechanism 6 is constituted by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A second speed drive gear 7 and a fourth speed drive gear 8 are mounted on the second input shaft 3 so as to be aligned and rotatable in the axial direction, and further to the second speed drive gear 7 and the second speed drive gear 7. The second speed drive gear 7 or another engagement mechanism 9 for selectively connecting the fourth speed drive gear 8 and the second input shaft 3 is provided between the fourth speed drive gear 8 and the axial direction. ing. Similar to the first input shaft engagement mechanism 6 described above, the engagement mechanism 9 is configured by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism.

  A first output shaft 10 and a second output shaft 11 are arranged in parallel with the first input shaft 2 and the second input shaft 3, and the first output shaft 10 and the second output shaft 11 have an input shaft 2, 2. A plurality of forward gear pairs that transmit torque to the motor 3 are provided. Specifically, on the first output shaft 10, a fourth speed driven gear 12 meshing with the fourth speed drive gear 8 is arranged coaxially and rotatably. A second speed driven gear 13 meshing with the second speed drive gear 7 is disposed on the first output shaft 10 so as to be rotatable coaxially. Is provided with a cylindrical shaft portion 13a extending in a direction opposite to the fourth speed driven gear 12. On the outer peripheral side of the cylindrical shaft portion 13a of the second-speed driven gear 13, a first output shaft idle gear 14 in which a first idle gear 14a and a second idle gear 14b are integrated, and a reverse drive gear 15 Are aligned in the axial direction and rotatably mounted. The second speed driven gear 13 is engaged with the second speed drive gear 7, the first idle gear 14 a is engaged with the third speed drive gear 5, and the second idle gear 14 b is engaged with the first speed drive gear 4. , And each forms a gear pair. Further, the first output shaft 10 has a fourth speed driven gear 12 or a second gear disposed between the fourth speed driven gear 12 and the second speed driven gear 13 in the axial direction thereof. A first output shaft engagement mechanism 16 that selectively connects the second-speed driven gear 13 and the first output shaft 10, and an end side of the cylindrical shaft portion of the second-speed driven gear 13 in the axial direction thereof And a reverse drive gear engagement mechanism 17 that connects the second speed driven gear 13 and the reverse drive gear 15. The first output shaft engagement mechanism 16 and the reverse drive gear engagement mechanism 17 are constituted by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A first output gear 18 is provided at the end of the first output shaft 10 opposite to the side where the reverse drive gear engagement mechanism 17 is provided, and this first output gear 18 is not shown. Power is transmitted to a drive wheel (not shown) via a differential gear.

  The second output shaft 11 includes a first speed driven gear 19, a third speed driven gear 20 meshed with the third speed drive gear 5, a third idle gear 21 a, and a fourth idle gear. The second output shaft idle gear 21 integrated with 21b is aligned in the axial direction and is rotatably attached. The first speed driven gear 19 is meshed with the first speed drive gear 4, the third idle gear 21 a is meshed with the second speed drive gear 7, and the fourth idle gear 21 b is meshed with the fourth speed drive gear 8. , And each forms a gear pair. Further, a reverse driven gear 22 for reverse travel is formed integrally with the first speed driven gear 19, and the reverse driven gear 22 meshes with the reverse drive gear 15. Further, the second output shaft 11 includes a reverse driven gear integrated with the first speed driven gear 19 between the first speed driven gear 19 and the third speed driven gear 20 in the axial direction thereof. 22 or a third driven gear 20 and a reverse driven gear engagement mechanism 23 for selectively connecting the second output shaft 11 to each other. The reverse driven gear engagement mechanism 23 is constituted by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A second output gear 24 is provided at the end of the second output shaft 11 opposite to the side where the reverse driven gear engagement mechanism 23 is provided, and the second output gear 24 is a differential (not shown). Power is transmitted to drive wheels (not shown) via gears.

  According to the above-described transmission according to the present invention, by inputting torque from the first input shaft 2 via the first clutch, a total of four shift stages, ie, 1, 3, 5, and 7, which are odd stages, are provided. Can be set. In addition, by inputting torque from the second input shaft 3 via the second clutch, a total of four speed stages, that is, 2, 4, 6, and 8, which are even stages, can be set. Therefore, the number of shift speeds that can be set is 8 in the forward speed. Further, by inputting torque from the second input shaft 3 via the second clutch and via the reverse drive gear 15 and the reverse driven gear 22, it is possible to set the first reverse speed.

  Next, the operation will be described. When the reverse gear is selected in the dual clutch transmission according to the present invention, the torque of the power source is input to the second input shaft 3 via the second clutch. Since the second input shaft 3 and the second speed drive gear 7 are coupled by another engagement mechanism 9, the torque transmitted to the second input shaft 3 meshes with the second speed drive gear 7. Is transmitted to the second speed driven gear 13. Further, since the second speed driven gear 13 is connected to the reverse drive gear 15 via the reverse drive gear engagement mechanism 17, the torque input to the second speed driven gear 13 is the reverse drive gear. 15 is transmitted to the reverse driven gear 22 meshing with the gear 15. Since the reverse driven gear 22 integrated with the first speed driven gear 19 is coupled to the second output shaft 11 via the reverse driven gear engagement mechanism 23, the reverse driven gear 22 is integrally provided on the second output shaft 11. The second output gear 24 transmits a torque transmitted from a power source to a driving wheel (not shown) via a differential gear (not shown), in other words, a rotation transmitted from the power source in a reverse rotation. Therefore, the reverse idler gear shaft for reverse driving is not required, the number of meshing gears is reduced, the power transmission efficiency is improved, and the transmission can be reduced in size and weight as much as possible.

  Further, in the dual clutch transmission according to the present invention, when the forward gear, particularly the second speed is selected, the torque of the power source is input to the second input shaft 3 via the second clutch. Since the second input shaft 3 and the second speed drive gear 7 are coupled by another engagement mechanism 9, the torque transmitted to the second input shaft 3 meshes with the second speed drive gear 7. Is transmitted to the second speed driven gear 13. Since the second speed driven gear 13 is connected to the first output shaft 10 via the first output shaft engaging mechanism 16, the torque input to the second speed driven gear 13 is the first output. It is transmitted to a first output gear 18 provided integrally with the shaft 10 and is transmitted to a driving wheel (not shown) via a differential gear (not shown). At this time, since the second speed driven gear 13 and the reverse drive gear 15 are not connected via the reverse drive gear engagement mechanism 17, the reverse drive gear 15 and the reverse driven gear 22 do not rotate, Power loss due to gear rotation can be reduced.

  When the reverse drive gear engaging mechanism 17 is engaged with the reverse drive gear 15 and the reverse drive gear 15 and the reverse driven gear 22 are capable of transmitting torque, the second speed drive gear 7 and the By not connecting the two input shafts 3 via the other engagement mechanisms 9, even if torque is input from the power source to the second input shaft 3 via the second clutch, the torque is used for the second speed change. It is not transmitted to the drive gear 7. Accordingly, the second gear drive gear 7 does not rotate, and the reverse drive gear 15 and the reverse driven gear 22 do not rotate, so that power loss due to the gear rotation can be reduced.

  Next, a description will be given of a second embodiment of the transmission according to the present invention. FIG. 2 shows a dual clutch transmission of 8 forward speeds and 1 reverse speed as in the first embodiment. Since the configuration related to each input shaft of the transmission 25 is substantially the same as the configuration related to each input shaft 2 and 3 in the first embodiment, the description thereof is omitted, and the first output shaft and the second output shaft are omitted. Only the structure concerning will be described.

  The first output shaft 26 has a fourth-speed driven gear 27 meshed with the fourth-speed drive gear 8 and a second-speed driven gear 28 meshed with the second-speed drive gear 7. The reverse drive gear 29 and the first output shaft idle gear 30 in which the first idle gear 30a and the second idle gear 30b are integrated are aligned in the axial direction and rotatably attached. Further, the second speed driven gear 28 is provided with a cylindrical shaft portion 28a, and a reverse drive gear 29 is rotatably attached to the outer peripheral side of the cylindrical shaft portion 28a. The second-speed driven gear 28 meshes with the second-speed drive gear 7, the first idle gear 30 a meshes with the third-speed drive gear 5, and the second idle gear 30 b becomes the first-speed drive gear 4. , And each forms a gear pair. Further, the first output shaft 26 has a fourth-speed driven gear 27 or a second gear arranged between the fourth-speed driven gear 27 and the second-speed driven gear 28 in the axial direction thereof. A first output shaft engagement mechanism 31 that selectively connects the second-speed driven gear 28 and the first output shaft 26, and between the second-speed driven gear 28 and the reverse drive gear 29 in the axial direction thereof. And a reverse drive gear engaging mechanism 32 for connecting the second speed driven gear 28 and the reverse drive gear 29. The first output shaft engagement mechanism 31 and the reverse drive gear engagement mechanism 32 are constituted by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A first output gear 33 is provided at the end of the first output shaft 26 opposite to the side on which the first output shaft idle gear 30 is provided, and this first output gear 33 is not shown. Power is transmitted to a drive wheel (not shown) via a differential gear.

  The second output shaft 34 is a second output shaft idler in which a first speed driven gear 35, a third speed driven gear 36, a third idle gear 37a, and a fourth idle gear 37b are integrated. A gear 37 is axially aligned and rotatably mounted. The first speed driven gear 35 meshes with the first speed drive gear 4, the third idle gear 37 a meshes with the second speed drive gear 7, and the fourth idle gear 37 b meshes with the fourth speed drive gear 8. , And each forms a gear pair. Further, a reverse driven gear 38 for reverse travel is integrally provided on the third speed driven gear 36, and the reverse driven gear 38 is meshed with the reverse drive gear 29. Further, the second output shaft 34 includes a reverse driven gear integrated with the third speed driven gear 36 between the first speed driven gear 35 and the third speed driven gear 36 in the axial direction thereof. 38 or a reverse driven gear engagement mechanism 39 for selectively connecting the first-speed driven gear 35 and the second output shaft 34 to each other. The reverse driven gear engagement mechanism 39 is configured by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A second output gear 40 is provided at the end of the second output shaft 34 opposite to the side where the reverse driven gear engagement mechanism 39 is provided. The second output gear 40 is a differential (not shown). Power is transmitted to drive wheels (not shown) via gears.

  According to the above-described transmission according to the present invention, by inputting torque from the first input shaft 2 via the first clutch, a total of four shift stages, ie, 1, 3, 5, and 7, which are odd stages, are provided. Can be set. In addition, by inputting torque from the second input shaft 3 via the second clutch, a total of four speed stages, that is, 2, 4, 6, and 8, which are even stages, can be set. Therefore, the number of shift speeds that can be set is 8 in the forward speed. Further, by inputting torque from the second input shaft 3 via the second clutch and via the reverse drive gear 29 and the reverse driven gear 38, the reverse gear can be set.

  In addition, the dual clutch transmission according to the present invention can obtain the same effects as those of the first embodiment.

  Next, a reference example of the transmission according to the present invention will be described. FIG. 3 shows a dual clutch transmission of 8 forward speeds and 1 reverse speed, as in the first embodiment. The configuration related to each input shaft and the first output shaft of the transmission 41 is substantially the same as the configuration related to each input shaft 2 and 3 and the first output shaft 10 in the first embodiment. Is omitted, and only the configuration relating to the second output shaft will be described.

  Three forward transmission gears are rotatably disposed on the second output shaft 42. Specifically, the second output shaft 42 includes a first speed driven gear 43, a third speed driven gear 44 meshed with the third speed drive gear 5, and a third idle gear 45a. And a second output shaft idle gear 45 in which the fourth idle gear 45b is integrated are aligned in the axial direction and are rotatably attached. The first speed driven gear 43 meshes with the first speed drive gear 4, the third idle gear 45 a meshes with the second speed drive gear 7, and the fourth idle gear 45 b engages with the fourth speed drive gear 8. , And each forms a gear pair. Further, a reverse driven gear 46 for reverse travel is integrally provided on the second output shaft 42, and the reverse driven gear 46 meshes with the reverse drive gear 15. Further, the second output shaft 42 has a first speed driven gear 43 or a third speed driven gear between the first speed driven gear 43 and the third speed driven gear 44 in the axial direction thereof. Another engagement mechanism 47 for selectively connecting the drive gear 44 and the second output shaft 42 is provided. The engagement mechanism 47 is configured by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A second output gear 48 is provided at the end of the second output shaft 42 opposite to the side where the reverse driven gear 46 is provided. The second output gear 48 is connected to a differential gear (not shown). The power is transmitted to drive wheels (not shown).

  According to the above-described transmission according to the present invention, by inputting torque from the first input shaft 2 via the first clutch, a total of four shift stages, ie, 1, 3, 5, and 7, which are odd stages, are provided. Can be set. In addition, by inputting torque from the second input shaft 3 via the second clutch, a total of four speed stages, that is, 2, 4, 6, and 8, which are even stages, can be set. Therefore, the number of shift speeds that can be set is 8 in the forward speed. Further, by inputting torque from the second input shaft 3 via the second clutch and via the reverse drive gear 15 and the reverse driven gear 46, it is possible to set the first reverse speed.

  Further, the dual clutch transmission according to the present invention does not require a reverse idler gear shaft for reverse movement, as in the first embodiment, and as a result, the number of gear meshes is reduced and power transmission is achieved. The efficiency is improved, and the transmission can be made as small and light as possible.

  Next, another reference example of the transmission according to the present invention will be described. FIG. 4 shows a dual clutch transmission of 8 forward speeds and 1 reverse speed as in the second embodiment. The configuration related to each input shaft and the first output shaft of the transmission 49 is substantially the same as the configuration related to the input shafts 2 and 3 and the first output shaft 26 in the third embodiment. Is omitted, and only the configuration relating to the second output shaft will be described.

  The second output shaft 50 is a second output shaft idler in which a first speed driven gear 51, a third speed driven gear 52, a third idle gear 53a, and a fourth idle gear 53b are integrated. A gear 53 is axially aligned and rotatably mounted. The first speed driven gear 51 is engaged with the first speed drive gear 4, the third idle gear 53 a is engaged with the second speed drive gear 7, and the fourth idle gear 53 b is engaged with the fourth speed drive gear 8. , And each forms a gear pair. The second output shaft 50 is integrally provided with a reverse driven gear 54 for reverse travel between the third speed driven gear 52 and the second output shaft idle gear 53 in the axial direction thereof. The reverse driven gear 54 meshes with the reverse drive gear 29. Further, the second output shaft 50 includes a third-speed driven gear 52 or a first-speed driven gear between the first-speed driven gear 51 and the third-speed driven gear 52 in the axial direction thereof. An engagement mechanism 55 that selectively connects the drive gear 51 and the second output shaft 50 is provided. The engagement mechanism 55 is constituted by, for example, a synchronizer or a multi-plate clutch that is a synchronization mechanism. A second output gear 56 is provided at the end of the second output shaft 50 opposite to the side where the engagement mechanism 55 is provided. The second output gear 56 is a differential gear (not shown). Power is transmitted to drive wheels (not shown) via

  According to the above-described transmission according to the present invention, by inputting torque from the first input shaft 2 via the first clutch, a total of four shift stages, ie, 1, 3, 5, and 7, which are odd stages, are provided. Can be set. In addition, by inputting torque from the second input shaft 3 via the second clutch, a total of four speed stages, that is, 2, 4, 6, and 8, which are even stages, can be set. Therefore, the number of shift speeds that can be set is 8 in the forward speed. Further, by inputting torque from the second input shaft 3 via the second clutch and via the reverse drive gear 29 and the reverse driven gear 52, it is possible to set the first reverse speed.

  Further, the dual clutch transmission according to the present invention does not require a reverse idler gear shaft for reverse movement, as in the first embodiment, and as a result, the number of gear meshes is reduced and power transmission is achieved. The efficiency is improved, and the transmission can be made as small and light as possible.

  DESCRIPTION OF SYMBOLS 1 ... Twin clutch type transmission, 2 ... 1st input shaft, 3 ... 2nd input shaft, 6, 9, 16, 23 ... Engagement mechanism, 10 ... 1st output shaft, 11 ... 2nd output shaft, 15 ... Reverse drive gear, 17 ... Reverse drive gear engagement mechanism, 22 ... Reverse driven gear, 23 ... Reverse driven gear engagement mechanism.

Claims (4)

The first input shaft and the second input shaft to which power is selectively transmitted from the driving force source via the clutch are arranged on the same axis, and the first output from which power is transmitted from these input shafts A shaft and a second output shaft are arranged in parallel to each of the input shafts, between the first input shaft, the first output shaft, and the second output shaft, as well as the second input shaft, the first output shaft, and the first output shaft. Twins in which a plurality of pairs of gears having different gear ratios are provided between the two output shafts, and a reverse gear pair for setting a reverse gear is provided between the first output shaft and the second output shaft. In clutch type transmission,
The reverse drive gear constituting the reverse gear pair is arranged on one of the output shafts, and the reverse drive gear and the other gear on the one output shaft can selectively transmit torque. A reverse drive engagement mechanism to be connected is provided,
A reverse driven gear that constitutes the reverse gear pair is disposed on one of the other output shafts, and the reverse driven gear and the other output shaft are selectively connected to each other so as to be able to transmit torque. A mechanism is provided,
The reverse drive engagement mechanism from the clutch selectively connecting one of the input shafts to the driving force source for transmitting the power output from the driving force source to the other gear on the one output shaft A twin clutch type transmission characterized in that another engagement mechanism capable of selectively interrupting transmission of torque is provided in a path for transmitting torque. Still another gear constituting a pair with the other gear on the one output shaft is rotatably supported by any one of the input shafts,
The other engagement mechanism includes a shift stage clutch that is provided on any one of the input shafts and engages the other gear and any one of the input shafts so that torque can be transmitted. The twin clutch transmission according to claim 1. The reverse driven gear is formed integrally with another gear included in the plurality of pairs of gears rotatably provided on the other output shaft, and
3. The twin clutch according to claim 1, wherein the reverse driven gear engagement mechanism includes a shift stage clutch that engages the other output shaft and the other gear so that torque can be transmitted. 4. Type transmission. The plurality of pairs of gears includes a first speed drive gear provided on the first input shaft and a first speed driven gear provided rotatably on the other output shaft. A transmission gear pair, a second speed transmission gear pair comprising a second speed drive gear provided on the second input shaft, and the other gear on the one output shaft; and the first input shaft. A third-speed transmission gear pair comprising a third-speed driving gear provided and a third-speed driven gear rotatably provided on the other output shaft; and a third-speed transmission gear pair rotatable on the second input shaft. A fourth-speed transmission gear pair comprising a fourth-speed drive gear provided and a fourth-speed driven gear rotatably provided on the one output shaft; the first-speed drive gear; A fifth speed transmission gear comprising an idle gear constituting a first output shaft idle gear rotatably provided on one output shaft A sixth speed transmission gear pair comprising: a second speed drive gear; and an idle gear constituting a second output shaft idle gear rotatably provided on the other output shaft; and the third speed gear A seventh speed transmission gear pair composed of a drive gear and another idle gear constituting the first output shaft idle gear, and another idle gear constituting the fourth speed drive gear and the second output shaft idle gear. An eighth speed transmission gear pair comprising a gear,
A first input shaft engagement mechanism that selectively connects the first speed drive gear or the third speed drive gear and the first input shaft so that torque can be transmitted; and the other on the one output shaft 2. A first output shaft engagement mechanism for selectively connecting the second gear or the fourth driven gear and the second output shaft so that torque can be transmitted. Twin clutch type transmission.

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