JP4922257B2 - transmission - Google Patents

Description

  The present invention includes at least a main shaft, a counter shaft and a secondary shaft arranged in parallel to each other, a first main gear is arranged on the main shaft, a first counter gear is arranged on the counter shaft, and the secondary shaft The present invention relates to a transmission having a first secondary gear disposed thereon.

In a manual transmission having an input shaft (main shaft) connected to the engine, an output shaft (counter shaft) connected to the drive wheels, and an intermediate shaft (secondary shaft) for shifting, the intermediate shaft is the input shaft. In order to maintain a constant rotation state in conjunction with the motor, the drive gear provided on the input shaft and the driven gear provided on the intermediate shaft are engaged with the idle gear provided on the output shaft, and the reverse gear is established to establish the reverse gear. Japanese Patent Application Laid-Open Publication No. 2004-228667 discloses an idle shaft that supports a reverse idle gear in addition to the shaft, the output shaft, and the intermediate shaft.
Japanese Patent Publication No. 5-53982

  By the way, in the above-mentioned conventional one, since it is necessary to provide an idle gear for transmitting a driving force from the input shaft to the intermediate shaft on the output shaft, there is a problem that the axial dimension of the output shaft increases. In addition, if an idle shaft for supporting the idle gear is provided separately, two idle shafts are required in addition to the idle shaft for supporting the reverse idle gear, which increases the number of parts and the transmission size. There is a problem.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to reduce the number of parts and the size of a transmission.

  In order to achieve the above object, according to the invention described in claim 1, at least a main shaft, a counter shaft and a secondary shaft arranged in parallel to each other are provided, and a first main gear is arranged on the main shaft, In the transmission in which the first counter gear is arranged on the counter shaft and the first secondary gear is arranged on the secondary shaft, the main shaft, the counter shaft, and the idle shaft arranged in parallel with the secondary shaft are moved forward. The first idle gear for the shift stage is fixed and the second idle gear for the reverse shift stage is detachably supported, and the first idle gear meshes with the first main gear and the first secondary gear, The second idle gear meshes with the first counter gear Transmission is proposed, characterized in that.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, a second secondary gear detachably supported by the secondary shaft meshes with the first counter gear. A transmission is proposed.

  According to a third aspect of the present invention, in addition to the configuration of the second aspect, a gear ratio from the second secondary gear to the first counter gear is greater than 1.0, and the second secondary gear A transmission is proposed in which a synchronous coupling device that engages and disengages the secondary shaft is disposed on the secondary shaft.

  The first-speed to second-speed synchronous coupling device S2 of the embodiment corresponds to the synchronous coupling device of the present invention, the main drive gear 11 of the embodiment corresponds to the first main gear of the present invention, and the secondary of the embodiment. The driven gear 14 corresponds to the first secondary gear of the present invention, the secondary first speed gear 15 of the embodiment corresponds to the second secondary gear of the present invention, and the counter first speed-reverse gear 19 of the embodiment corresponds to the present invention. Corresponding to the first counter gear, the forward idle gear 23 of the embodiment corresponds to the first idle gear of the present invention, and the reverse idle gear 24 of the embodiment corresponds to the second idle gear of the present invention.

  According to the configuration of the first aspect, the first idle gear for the forward shift stage is fixed to the idle shaft and the second idle gear for the reverse shift stage is detachably supported, and the first idle gear is attached to the main shaft. Since the first main gear and the first secondary gear of the secondary shaft are engaged, and the second idle gear is engaged with the first counter gear of the counter shaft, the idle shaft for supporting the first idle gear for forward movement is used. Thus, it becomes possible to support the second idle gear for reverse travel, which can contribute to the reduction in the number of parts and the cost and the downsizing of the transmission.

  According to the second aspect of the present invention, since the second secondary gear detachably supported by the secondary shaft meshes with the first counter gear, the first counter gear is moved forward through the second secondary gear. And the establishment of the reverse gear stage via the second idle gear, which can contribute to a reduction in the number of parts and a reduction in the axial dimension of the transmission.

  According to the third aspect of the present invention, since the gear ratio from the second secondary gear to the first counter gear is larger than 1.0, the torque applied to the first counter gear is greater than the torque applied to the second secondary gear. However, since the second secondary gear having a smaller torque is engaged and disengaged by the synchronous coupling device provided on the secondary shaft, durability can be ensured while reducing the capacity of the synchronous coupling device.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  1 and 2 show an embodiment of the present invention. FIG. 1 is a view of a manual transmission viewed in the axial direction, and FIG. 2 is a sectional view taken along line 2-2 of FIG.

  As shown in FIG. 1 and FIG. The reverse first-speed manual transmission T includes a main shaft MS connected coaxially to the engine E via a dry single-plate clutch C, a secondary shaft SS, a counter shaft CS, and an idle shaft IS arranged in parallel with the main shaft MC. And a differential gear D connected to the countershaft CS.

  A main drive gear 11 is fixed to the main shaft MS, and a main 5-speed gear 12 and a main 6-speed gear 13 which are selectively coupled to the main shaft MS by the 5-speed-6-speed synchronous coupling device S1 are relatively rotated. It is supported freely.

  The secondary driven gear 14 is fixed to the secondary shaft SS, and the secondary first speed gear 15 and the secondary second speed gear 16 that are selectively coupled to the secondary shaft SS by the first speed-second speed synchronous coupling device S2 are relatively rotatable. The secondary 3rd gear 17 and the secondary 4th gear 18 that are selectively coupled to the secondary shaft SS by the 3rd-4th gear synchronous coupling device S3 are supported so as to be relatively rotatable.

  The counter shaft CS includes a counter first speed-reverse gear 19 that meshes simultaneously with the secondary first speed gear 15 and a reverse idle gear 24 described later, a counter second speed gear 20 that meshes with the secondary second speed gear 16, and a secondary third speed gear 17. A counter 3rd-5th gear 21 that meshes simultaneously with the main 5th gear 12 and a counter 4th-6th gear 22 that meshes simultaneously with the secondary 4th gear 18 and the main 6th gear 13 are fixed.

  The idle shaft IS is fixedly provided with a forward idle gear 23 that meshes with the main drive gear 11 and the secondary driven gear 14 at the same time, and is selectively coupled to the idle shaft IS by the reverse synchronous coupling device S4 to be counter 1st speed-reverse gear. A reverse idle gear 24 meshing with the gear 19 is supported.

  A final drive gear 25 fixed to the countershaft CS meshes with a final driven gear 26 provided to the differential gear D, and left and right drive wheels W, W are connected to drive shafts 27, 27 extending from the differential gear D to the left and right.

  Next, the operation of the first embodiment of the present invention having the above configuration will be described.

  When the dry single-plate clutch C is engaged, the rotation of the engine E is transmitted to the main shaft MS at the same speed, and the rotation of the engine E is transmitted through the path of the main drive gear 11 → forward idle gear 23 → secondary driven gear 14 to the secondary shaft SS. The secondary shaft SS is rotated at a lower speed than the main shaft MS.

  When the secondary 1st gear 15 is coupled to the secondary shaft SS by the 1st-2nd gear synchronous coupling device S2, the rotation of the engine E is dry single plate clutch C → main shaft MS → main drive gear 11 → forward idle gear 23 → secondary driven gear. 14 → secondary shaft SS → first speed-2 speed synchronous coupling device S2 → secondary first speed gear 15 → counter first speed−reverse gear 19 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shaft 27 , 27 are transmitted to the drive wheels W, W, and the first gear is established.

  When the secondary 2nd gear 16 is coupled to the secondary shaft SS by the 1st-2nd gear synchronous coupling device S2, the rotation of the engine E is dry single plate clutch C → main shaft MS → main drive gear 11 → forward idle gear 23 → secondary driven gear. 14 → secondary shaft SS → first speed-2 speed synchronous coupling device S2 → secondary second speed gear 16 → counter second speed gear 20 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shafts 27 and 27 Is transmitted to the drive wheels W, W, and the second gear is established.

  When the secondary 3rd speed gear 17 is coupled to the secondary shaft SS by the 3rd speed-4th gear synchronous coupling device S3, the rotation of the engine E is dry single plate clutch C → main shaft MS → main drive gear 11 → forward idle gear 23 → secondary driven gear. 14 → secondary shaft SS → 3-speed-4th-speed synchronous coupling device S3 → secondary 3-speed gear 17 → counter 3-speed-5-speed gear 21 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shaft 27 and 27 are transmitted to the drive wheels W and W to establish a third gear.

  When the secondary 4-speed gear 18 is coupled to the secondary shaft SS by the 3-speed 4-speed synchronous coupling device S3, the rotation of the engine E is dry single-plate clutch C → main shaft MS → main drive gear 11 → forward idle gear 23 → secondary driven gear. 14 → secondary shaft SS → 3-speed-4th-speed synchronous coupling device S3 → secondary 4-speed gear 18 → counter 4-speed-6-speed gear 22 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shaft 27 and 27 are transmitted to the drive wheels W and W to establish the fourth gear.

  When the main 5-speed gear 12 is coupled to the main shaft MS by the 5-speed-6-speed synchronous coupling device S1, the rotation of the engine E is the dry single plate clutch C → the main shaft MS → the 5-speed-6-speed synchronous coupling device S1 → the main 5 5th speed transmission is transmitted to the drive wheels W and W through the path of the speed gear 12 → counter 3rd speed-5th speed gear 21 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shafts 27 and 27 A stage is established.

  When the main 6-speed gear 13 is coupled to the main shaft MS by the 5-speed-6-speed synchronous coupling device S1, the rotation of the engine E is the dry single-plate clutch C → main shaft MS → 5-speed-6-speed synchronous coupling device S1 → main 6 6-speed transmission is transmitted to the drive wheels W and W through the path of the speed gear 13 → counter 4th speed-6th speed gear 22 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shafts 27 and 27. A stage is established.

  When the reverse idle gear 24 is coupled to the idle shaft IS by the reverse synchronous coupling device S4, the rotation of the engine E is dry single plate clutch C → main shaft MS → main drive gear 11 → forward idle gear 23 → idle shaft IS → reverse synchronous coupling. Reverse rotation to drive wheels W and W through the path of device S4 → reverse idle gear 24 → first counter-reverse gear 19 → counter shaft CS → final drive gear 25 → final driven gear 26 → differential gear D → drive shafts 27 and 27 Then, the reverse gear is established.

  As described above, according to the present embodiment, the reverse idle gear 24 that has been conventionally supported by the dedicated reverse idle shaft is supported by the forward idle gear 23 that transmits the rotation of the main shaft MS to the secondary shaft SS. Therefore, not only the number of parts and cost can be reduced, but also the manual transmission T can be reduced in size.

  Further, the counter first speed-reverse gear 19 fixed to the countershaft CS simultaneously meshes with the secondary first speed gear 15 and the reverse idle gear 24, and is commonly used for establishing the first gear and the reverse gear. Therefore, it is possible to reduce the number of parts, the cost, and the manual transmission T in the axial direction.

  Similarly, the counter 3rd-5th gear 21 fixed to the countershaft CS simultaneously meshes with the main 5th gear 12 and the secondary 3rd gear 17 to establish the 3rd gear and the 5th gear. The counter 4th-6th gear 22 shared by the countershaft CS and fixed to the countershaft CS is simultaneously meshed with the main 6th gear 13 and the secondary 4th gear 18 to establish the 4th gear and 6th gear. Since it is shared with the establishment of the stage, it is possible to reduce the number of parts, the cost, and the manual transmission T in the axial direction.

  Further, when the fifth gear and the sixth gear are established, the rotational speed of the main shaft MS on the drive side is higher than the rotational speed of the counter shaft CS on the driven side, so the torque of the main shaft MS is greater than the torque of the counter shaft CS. Also lower. Therefore, by arranging the 5-speed-6-speed synchronous coupling device S1 on the main shaft MS side having a low torque, it is possible to ensure the durability while keeping the capacity small.

  Similarly, the rotational speed of the secondary shaft SS on the drive side is higher than the rotational speed of the counter shaft CS on the driven side when the first speed stage and the second speed stage are established and when the third speed stage and the fourth speed stage are established. Therefore, the torque of the secondary shaft SS is lower than the torque of the counter shaft CS. Therefore, the durability can be ensured while keeping the capacity small by disposing the first-speed / second-speed synchronous coupling device S2 and the third-speed / four-speed synchronous coupling device S3 on the secondary shaft SS with low torque.

  As is clear from FIG. 1, the countershaft CS having no synchronous coupling device is arranged at the lowest position, and the main shaft MS, the secondary shaft SS, and the idle shaft IS having the synchronous coupling devices S1 to S4 are more than the countershaft CS. Since they are arranged at a high position, the structure of the link and fork of the transmission system can be simplified.

  As mentioned above, although embodiment of this invention was explained in full detail, this invention can perform a various design change in the range which does not deviate from the summary.

  For example, in the embodiment, the manual transmission T with six forward speeds and one reverse speed is illustrated, but the number of shift speeds that can be established is arbitrary.

  Although the manual transmission T is exemplified in the embodiment, the present invention is applicable to an automatic transmission and an automatic manual transmission in which the dry single-plate clutch C of the manual transmission and the synchronous coupling devices S1 to S4 are driven by actuators. Can be applied.

View of manual transmission in axial direction 2-2 sectional view of FIG.

Explanation of symbols

MS Main shaft CS Counter shaft SS Secondary shaft IS Idle shaft S2 1st-2nd gear synchronous coupling device (synchronous coupling device)
11 Main drive gear (first main gear)
14 Secondary driven gear (first secondary gear)
15 Secondary 1st gear (2nd secondary gear)
19 Counter 1 speed-reverse gear (first counter gear)
23 Forward idle gear (first idle gear)
24 Reverse idle gear (second idle gear)

Claims (3)

At least a main shaft (MS), a counter shaft (CS) and a secondary shaft (SS) arranged in parallel to each other;
A first main gear (11) is disposed on the main shaft (MS), a first counter gear (19) is disposed on the counter shaft (CS), and a first secondary gear ( 14) In the transmission where
A first idle gear (23) for a forward shift stage is fixed to an idle shaft (IS) arranged in parallel with the main shaft (MS), the counter shaft (CS), and the secondary shaft (SS), and the vehicle moves backward. A second idle gear (24) for the shift stage is detachably supported;
The first idle gear (23) meshes with the first main gear (11) and the first secondary gear (14), and the second idle gear (24) meshes with the first counter gear (19). Transmission characterized by.   The transmission according to claim 1, characterized in that a second secondary gear (15) removably supported by the secondary shaft (SS) meshes with the first counter gear (19).   Synchronous coupling in which a gear ratio from the second secondary gear (15) to the first counter gear (19) is larger than 1.0, and the second secondary gear (15) is engaged with and disengaged from the secondary shaft (SS). Transmission according to claim 2, characterized in that the device (S2) is arranged on the secondary shaft (SS).

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