JP2009030753A - Transmission with six pairs of forward travel shift gears - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission with six pairs of forward travel shift gears, having a shorter axial length. <P>SOLUTION: First and second intermediate shafts 16, 17 are arranged on one input shaft 15. A first gear transmission mechanism 20A provided between the input shaft and the first intermediate shaft consists of pairs of first-third forward travel shift gears 21a, 21b, 22a, 22b, 23a, 23b, a first change-over clutch 30A provided on one side of the pair of first forward shift gears, and a second change-over clutch 30B provided between the pairs of second and third forward travel shift gears. A second gear transmission mechanism 20B provided between the input shaft and the second intermediate shaft similarly consists of pairs of fourth-sixth forward travel shift gears 24a, 24b, 25a, 25b, 26a, 26b, a third change-over clutch 30C, and a fourth change-over clutch 30D. The first change-over clutch and the pair of first forward travel shift gears, and the third change-over clutch and the pair of fourth forward travel shift gears are arranged mutually opposing each other in the axial direction. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a multi-stage transmission for a vehicle, and more particularly, to a transmission having six forward transmission gear pairs in which the axial length of the transmission is shortened.

  For example, in a front engine front drive type vehicle in which an engine and a transmission arranged in series with each other are arranged horizontally, two intermediates are provided for one input shaft in order to make the transmission compact and increase the torque. By providing a shaft and arranging a plurality of transmission gear pairs in parallel between the input shaft and each intermediate shaft, the axial length of the transmission is shortened and the number of shift stages is increased. FIG. 4 shows an example of such a transmission having six forward transmission gear pairs. In this transmission 1, the input shaft 3a and the first and second intermediate shafts 3b, 3c are arranged in parallel in the transmission case 2, and the first speed to the first shaft 3b are interposed between the input shaft 3a and the first intermediate shaft 3b. A fourth speed gear pair is provided, and first and second switching clutches 5A and 5B are provided between the first speed gear pair and the second speed gear pair and between the third speed gear pair and the fourth speed gear pair, respectively. Further, a fifth speed gear pair and a sixth speed gear pair are provided between the input shaft 3a and the second intermediate shaft 3c, and a third switching clutch 5C is provided between them, and the input shaft 3a is rotationally driven by the engine, The first intermediate shaft 3b and the second intermediate shaft 3c are connected to the output shafts 8a and 8b via the final reduction gear trains 6a, 6b and 6c and the differential mechanism 7. In the example shown in FIG. 4, a reverse gear transmission mechanism 4C comprising a reverse gear train and a reverse switching clutch 5D is provided between the input shaft 3a, the reverse shaft 3d arranged in parallel therewith, and the second intermediate shaft 3c. It has been.

As shown in FIG. 3, the transmission 1 shown in FIG. 4 is arranged and fixed in series on the rear side in the axial direction of the engine 10, and its input shaft 3a is connected to the output shaft of the engine 10 via a clutch. ing. The transmission 1 shown in FIG. 4 is shown as a comparative example and is not necessarily a known technique, but a similar technique is disclosed in Patent Document 1.
JP 2002-70960 A (paragraphs [0032] to [0035], FIGS. 5 and 6).

  In the transmission having the six forward transmission gear pairs shown in the comparative example of FIG. 4, the first gear transmission mechanism 4A and the second gear transmission are provided between the input shaft 3a and the two intermediate shafts 3b and 3c as described above. Since the mechanism 4B is arranged in parallel, the total length of the transmission 1 can be shortened as compared with the case where the gear transmission mechanism is arranged between the input shaft and one intermediate shaft if the number of shift stages is the same. . However, since four sets of forward transmission gear pairs and two sets of switching clutches 5A and 5B are disposed on the first intermediate shaft 3b, two sets of forward transmission gear pairs, one set of reverse gear trains, and two sets of forward clutch gears are arranged. Compared to the second intermediate shaft 3c on which the switching clutches 5C and 5D are arranged, the length is increased by one gear, and a corresponding amount of wasted space is generated in the second intermediate shaft 3c. An object of the present invention is to eliminate such a useless space and reduce the length of the transmission in the axial direction (see the length L in FIG. 3).

  For this purpose, a transmission having six forward transmission gear pairs according to the present invention is arranged in parallel with an input shaft that is rotationally driven by an engine, an output shaft that is connected to a drive wheel, and an output shaft. A first intermediate shaft and a second intermediate shaft coupled to the shaft; a first gear transmission mechanism provided between the input shaft and the first intermediate shaft and including a plurality of gear pairs and a switching clutch; the input shaft and the second intermediate shaft; In a transmission having six sets of forward transmission gear pairs provided between a middle shaft and provided with a second gear transmission mechanism comprising a plurality of gear pairs and a switching clutch, the first gear transmission mechanism includes an input shaft and a first gear transmission mechanism. The first to third forward transmission gear pairs provided between one intermediate shaft and the input shaft and the first intermediate shaft provided on one side of the first forward transmission gear pair. A first switching clutch for switching the power transmission of the second, second and 3 is a second switching clutch that is provided between the three forward transmission gear pairs and switches power transmission between the input shaft and the first intermediate shaft by the two forward transmission gear pairs. 4 to 6 forward transmission gear pairs provided between the second intermediate shaft and an input shaft and a second intermediate shaft provided on one side of the fourth forward transmission gear pair. Between the input shaft and the second intermediate shaft by the two forward transmission gear pairs provided between the third switching clutch for switching the power transmission between the fifth forward transmission gear pair and the fifth and sixth forward transmission gear pairs. The fourth switching clutch for switching, the first switching clutch and the fourth forward transmission gear pair, the third switching clutch and the first forward transmission gear pair, and the second switching clutch and the fourth switching clutch are respectively connected to the input shaft. In the axial direction, each pair with each other Is characterized in that arranged so that the position of.

  The transmission having the six forward transmission gear pairs described in the previous section is provided between a reverse shaft disposed in parallel with the input shaft and connected to the output shaft, and between the input shaft, the second intermediate shaft, and the reverse shaft. And a reverse gear transmission mechanism comprising a reverse gear train comprising a drive gear, an idle gear and a driven gear, and a reverse gear transmission mechanism comprising a reverse switching clutch. The driven gear is rotatably provided on the reverse shaft and can be separated by the reverse switching clutch. The drive gear and the idler gear are preferably used in common with the first forward transmission gear pair or the fourth forward transmission gear pair.

  In the transmission having the six forward transmission gear pairs described in the preceding paragraph, the first forward transmission gear pair or the fourth forward transmission gear pair is preferably a second speed gear pair or a first speed gear pair. .

  In the transmission having the six forward transmission gear pairs described in the preceding item 2, the first forward transmission gear pair or the fourth forward transmission gear pair is disposed closer to the engine than the remaining forward transmission gear pairs. Is preferred.

  In the transmission having the six forward transmission gear pairs described in the preceding paragraphs, the transmission is preferably arranged in series with the engine and integrally connected to each other.

  According to the first aspect of the present invention, the first gear transmission mechanism includes the first to third forward transmission gear pairs, the first switching clutch that switches the power transmission by the first forward transmission gear pair, the second and second And a second gear transmission mechanism for switching power transmission by the fourth to sixth forward transmission gear pairs and the fourth forward transmission gear pair. A third switching clutch, a fourth switching clutch for switching power transmission by the fifth and sixth forward transmission gear pairs, a first switching clutch and a fourth forward transmission gear pair, a third switching clutch and a first forward transmission gear. The gear pair and the second switching clutch and the fourth switching clutch are arranged so as to correspond to each other in the axial direction of the input shaft, whereby the first switching clutch and the fourth switching clutch are arranged. Advance transmission gear pair, third switching clutch and first forward transmission gear pair, second switching clutch and fourth switching clutch, second forward transmission gear pair and fifth forward transmission gear pair, third forward transmission gear Each of the pair and the sixth forward transmission gear pair is in a position corresponding to each other in the axial direction of the input shaft. Therefore, the number of forward transmission gear pairs and switching clutches provided on the first intermediate shaft and the second intermediate shaft is as follows. Since both are the same and can be arranged without any gap, the axial length of the entire transmission can be shortened. The first forward transmission gear pair and the first switching clutch, and the fourth forward transmission gear pair and the third switching clutch are arranged in the opposite directions in the axial direction, and each drive gear of the first and fourth forward transmission gear pairs. Are not shared, the gear ratios of the first and fourth forward transmission gear pairs can be freely selected, so that the change between the gear ratios of the respective gears can be set appropriately. it can.

  A reverse gear arranged parallel to the input shaft and connected to the output shaft, a reverse gear train including a drive gear, a freewheeling gear and a driven gear provided between the input shaft, the second intermediate shaft and the reverse shaft, and reverse A reverse gear transmission mechanism comprising a switching clutch is further provided. The driven gear is rotatably provided on the reverse shaft and is detachably connected to the reverse shaft by the reverse switching clutch. The drive gear and the idle gear are the first gear. According to the invention of claim 2 that is shared with the forward transmission gear pair or the fourth forward transmission gear pair, the reverse gear transmission mechanism can be provided without increasing the axial length of the transmission, Moreover, the structure can be simplified by reducing the number of gears by the number of shared gears.

  According to the invention described in the preceding item, the first forward transmission gear pair or the fourth forward transmission gear pair is a second speed gear pair or a first speed gear pair. Since the drive gear has a small diameter, a reverse gear train having a large reduction ratio can be easily obtained.

  According to the invention described in item 2, the first forward transmission gear pair or the fourth forward transmission gear pair is arranged on the engine side with respect to the remaining forward transmission gear pairs. Since the length in the axial direction of the transmission at the portion where the clutch is disposed can be reduced as compared with the length of the other portions, the transmission can be made more compact though it is partially.

  Further, according to the invention of claim 5 in which the transmissions of the inventions described in the preceding paragraphs are arranged in series with the engine and integrally connected to each other, the engine and the transmission, which tend to increase in overall length, are connected in series. An increase in the length of the drive unit can be reduced.

  The best mode of a transmission having six forward speeds according to the present invention will be described below with reference to FIGS. As shown mainly in FIGS. 1 and 2, the transmission 11 includes a transmission case 12, an input shaft 15 that is arranged in parallel to each other and is rotatably supported in the transmission case 12, a first intermediate shaft 16, The second intermediate shaft 17 and the reverse shaft 18, the first gear transmission mechanism 20 </ b> A provided between the input shaft 15 and the first intermediate shaft 16, and the first gear transmission mechanism 20 </ b> A provided between the input shaft 15 and the second intermediate shaft 17. A two-gear transmission mechanism 20B, a reverse gear transmission mechanism 20C provided between the input shaft 15, the second intermediate shaft 17 and the reverse shaft 18, an output shaft 19 connected to the drive wheels, and the output shaft 19 Reduction gear trains 28a, 28b, 28c, and 28d that connect the first intermediate shaft 16, the second intermediate shaft 17 and the reverse shaft 18 are provided. Most of the shafts 15 to 19, the gear transmission mechanisms 20 </ b> A to 20 </ b> C, the reduction gears 28 a to 28 d and the differential mechanism 29 are covered with the transmission case 12. As shown mainly in FIG. 2, the second intermediate shaft 17 and the reverse shaft 18 are positioned above the input shaft 15 and the first intermediate shaft 16.

  As shown in FIGS. 1 and 3, the transmission 11 is arranged in series on one side in the axial direction of the engine 10, the transmission case 12 is fixed to the engine 10, and the input shaft 15 is connected via a clutch (not shown). And connected to the crankshaft of the engine 10. The output shaft 19 of the transmission 11 is composed of two portions 19 a and 19 b that are arranged in a straight line and whose intermediate portions are connected via a differential mechanism 29, and both the portions 19 a and 19 b are rotated by the transmission case 12. While being supported freely, each outer end portion is connected to each drive wheel (not shown) via a joint and a drive shaft. The intermediate shafts 16, 17 and the reverse shaft 18 are engaged with a reduction large gear 28 d provided in a differential mechanism 29 by small reduction gears 28 a, 28 b, 28 c fixed to the ends on the engine 10 side. And connected to the output shaft 19.

  The first gear transmission mechanism 20A forms the second, fifth, and sixth speed stages for shifting. As shown in FIGS. 1 and 2, the first gear transmission mechanism 20A is provided between the input shaft 15 and the first intermediate shaft 16. The three gear pairs 21a, 21b, 22a, 22b and 23a, 23b, the first switching clutch 30A, and the second switching clutch 30B are provided. The three gear pairs of the first gear transmission mechanism 20A are a second speed gear pair (first forward transmission gear pair) 21a, 21b and a fifth speed gear pair (second forward transmission gear pair) 22a, 22b. And a sixth speed gear pair (third forward transmission gear pair) 23a, 23b. The drive gears 21a, 22a, 23a of each transmission gear pair are fixed to the input shaft 15, and their driven gears 21b, 22b, 23b. Is rotatably supported on the first intermediate shaft 16. The first switching clutch 30A is provided on the first intermediate shaft 16 on one side of the second speed driven gear 21b, and the second switching clutch 30B is provided on the fifth intermediate gear 16 and the sixth speed driven gear 22b, It is provided at a position between 23b.

  The first switching clutch 30A comprises a known synchromesh mechanism. The clutch hub O is fixed to the first intermediate shaft 16, the sleeve M is spline-engaged on the outer periphery of the clutch hub O in the axial direction, and the clutch hub. An engagement member S1 fixed to the second speed driven gear 21b located on one side of O is provided. If the sleeve M of the first switching clutch 30A is shifted leftward from the neutral position shown in the figure by a shift fork N that is manually or automatically operated, the sleeve M is spline-engaged with the engagement member S1, and the second speed gear pair. When the driven gear 21b of 21a, 21b is engaged with the first intermediate shaft 16 to form the second speed stage, and the sleeve M is returned to the neutral position, the driven gear 21b is disengaged from the first intermediate shaft 16 and Second gear is released.

  The second switching clutch 30B includes a clutch hub O that is fixed to the first intermediate shaft 16, a sleeve M that is spline-engaged on the outer periphery of the clutch hub O, and a fifth speed that is located on both sides of the clutch hub O. And engaging members S2 and S3 fixed to the sixth speed driven gears 22b and 23b, respectively. When the sleeve M of the second switching clutch 30B is shifted rightward from the neutral position in the figure by the shift fork N, it is spline-engaged with the engaging member S2, and the fifth speed driven gear 22b is engaged with the first intermediate shaft 16. Combined to form the fifth gear. If the sleeve M is shifted leftward from this state, the driven gear 22b is disengaged from the first intermediate shaft 16 and the fifth speed is released. If the sleeve M is further shifted leftward, the engagement member S3 is engaged. The sixth speed driven gear 23b is engaged with the first intermediate shaft 16 to form the sixth speed stage. When the sleeve M is returned to the neutral position, the driven gear 23b is detached from the first intermediate shaft 16 and the sixth speed is released.

  The second gear transmission mechanism 20B forms the first, third, and fourth speed stages for shifting. Like the first gear transmission mechanism 20A, the second gear transmission mechanism 20B is provided between the input shaft 15 and the second intermediate shaft 17. The three pairs of gears 24a, 24b, 25a, 25b and 26a, 26b, a third switching clutch 30C, and a fourth switching clutch 30D are provided. As in the case of the first gear transmission mechanism 20A, the three gear pairs of the second gear transmission mechanism 20B are a first speed gear pair (fourth forward transmission gear pair) 24a, 24b and a third speed gear pair ( A fifth forward transmission gear pair) 25a, 25b and a fourth speed gear pair (sixth forward transmission gear pair) 26a, 26b are included. The structure of the second gear transmission mechanism 20B is substantially the same as that of the first gear transmission mechanism 20A. If the sleeve M of the third switching clutch 30C is shifted rightward from the neutral position shown in the figure by the shift fork N, When the first speed driven gear 24b is engaged with the second intermediate shaft 17 to form the first speed stage and the sleeve M is returned to the neutral position, the driven gear 24b is The first gear is released by being disengaged from the intermediate shaft 17. Further, when the sleeve M of the fourth switching clutch 30D is shifted rightward from the illustrated neutral position by the shift fork N, it is splined to the engaging member S5, and the third speed driven gear 25b is connected to the second intermediate shaft 17. If the third gear is engaged and shifted to the left, the fourth gear 26b is engaged with the second intermediate shaft 17 after the third gear is released in the same manner as described above. If the fourth gear is formed and returned to the neutral position, the fourth gear is released.

  The first switching clutch 30A is disposed on the engine 10 side with respect to the second speed gear pair 21a, 21b. Conversely, the third switching clutch 30C is disposed on the opposite side of the engine 10 with respect to the first speed gear pair 24a, 24b. Has been. Thus, the first switching clutch 30A and the first speed gear pair (fourth forward transmission gear pair) 24a, 24b are arranged so as to correspond to each other in the axial direction of the input shaft 15, and the third switching clutch. 30C and the second speed gear pair (first forward transmission gear pair) 21a and 21b are arranged so as to correspond to each other in the axial direction of the input shaft 15, so that the second speed fixed to the input shaft 15 The drive gear 21a and the first speed drive gear 24a are separate and are not shared. Further, the second switching clutch 30B and the fourth switching clutch 30D are arranged so as to correspond to each other in the axial direction of the input shaft 15, whereby the fifth speed gear pair 22a, 22b and the third speed are set. The gear pair 25a, 25b, the sixth speed gear pair 23a, 23b and the fourth speed gear pair 26a, 26b are arranged at corresponding positions in the axial direction of the input shaft 15, and the fifth speed drive gear 22a and the third speed The drive gear 25a, the sixth speed drive gear 23a, and the fourth speed drive gear 26a are shared with each other.

  The reverse gear speed change mechanism 20C forms the reverse speed of the speed change, and as shown in FIGS. 1 and 2, the reverse gear trains 27a and 27b provided between the input shaft 15, the second intermediate shaft 17 and the reverse shaft 18 are provided. , 27c and a reverse switching clutch 30E. The reverse gear train includes a drive gear 27a fixed to the input shaft 15, an idle gear 27b and a driven gear 27c rotatably supported by the second intermediate shaft 17 and the reverse shaft 18, respectively. The idle gear 27b is shared with the drive gear 24a and the driven gear 24b of the first speed gear pair. The reverse switching clutch 30E provided on the reverse shaft 18 on the opposite side of the driven gear 27c from the engine 10 has the same structure as the first switching clutch 30A, and the sleeve M is shifted rightward from the neutral position shown in the figure by the shift fork N. When shifted, the engagement member SR is spline-engaged, and the driven gears 27c of the reverse gear trains 27a, 27b, 27c are engaged with the reverse shaft 18 to form a reverse gear, which is shifted in the reverse direction to the neutral position. If it is returned to, the reverse gear is released.

  According to the above-described embodiment, the first switching clutch 30A and the first speed gear pair 24a, 24b are arranged so as to correspond to each other in the axial direction of the input shaft 15, and the third switching clutch 30C and the second speed clutch The gear pairs 21a and 21b are arranged so as to correspond to each other in the axial direction of the input shaft 15, and the second switching clutch 30B and the fourth switching clutch 30D, the fifth speed gear pair 22a and 22b, and the third speed gear. The pair 25a, 25b, the sixth speed gear pair 23a, 23b, and the fourth speed gear pair 26a, 26b are arranged at corresponding positions in the axial direction of the input shaft 15, respectively. Accordingly, the number of forward transmission gear pairs and the number of switching clutches provided on the first intermediate shaft 16 and the second intermediate shaft 17 are 3 sets and 2 sets, respectively, and they are arranged without gaps, and 4 sets are provided on the first intermediate shaft 3b. Compared to the comparative example shown in FIG. 4 in which the forward transmission gear pair and two sets of switching clutches 5A and 5B are arranged, the operating stroke of the sleeve M of one gear and the first and third switching clutches 30A and 30C The length in the axial direction of the transmission (refer to the length L in FIG. 3) can be shortened by an amount equal to half. As a result, the engine and the transmission can be mounted even when the mounting space of the vehicle body is reduced in order to reduce the size of the vehicle, improve the collision safety performance, and improve the vehicle rigidity.

  Also, in this type of transmission in which two intermediate shafts are provided for one input shaft and a plurality of forward transmission gear pairs are arranged in parallel between the input shaft and each intermediate shaft, If the drive gear of the forward transmission gear pair provided between the intermediate shafts and the drive gear of the forward transmission gear pair provided between the input shaft and the other intermediate shaft are shared, the drive gear provided on the input shaft is reduced, so that the speed change The length of the machine in the axial direction can be shortened, but the degree of freedom in selecting the gear ratio is reduced, and the gear ratio between the gears cannot be changed to a desired state (for example, a geometric series). There is. However, in the above-described embodiment, the first switching clutch 30A and the first speed gear pair 24a, 24b and the third switching clutch 30C and the second speed gear pair 21a, 21b are arranged as described above, so that the input shaft 15 Since the fixed second speed drive gear 21a and the first speed drive gear 24a are not shared, the above-mentioned problem that the degree of freedom of selection of the gear ratio is reduced can be avoided, and a wasteful space can be avoided. It does not occur.

  In the above-described embodiment, the drive gear 27a and the idle gear 27b of the reverse gear trains 27a, 27b, and 27c are shared with the drive gear 24a and the driven gear 24b of the first speed gear pair 24a and 24b. If the reverse gear is provided, the axial length of the transmission will not increase, and the number of gears can be reduced by the number of shared gears, and the structure can be simplified. Since the drive gear 27a has a small diameter, a reverse gear train having a large reduction ratio can be easily obtained. Note that the drive gear 27a and the idle gear 27b of the reverse gear train are replaced with the drive gear 21a and the driven gear 21b of the second gear pair 21a and 21b instead of the drive gear 24a and the driven gear 24b of the first gear pair 24a and 24b. The same effect can be obtained by doing so. Furthermore, in the above-described embodiment, the first speed gear pair 24a, 24b is disposed closer to the engine 10 than the remaining forward transmission gear pairs, and in this way, the transmission of the portion of the transmission where the reverse switching clutch 30E is disposed. Since the axial length can be made smaller than the length of the other portions, the transmission can be made more compact in spite of a part. Similar effects can be obtained by arranging the second speed gear pair 21a, 21b closer to the engine 10 than the remaining forward transmission gear pairs.

  In the above-described embodiment, the first forward transmission gear pair 21a, 21b is the second speed gear pair, the second forward transmission gear pair 22a, 22b is the fifth speed gear pair, and the third forward transmission gear pair. 23a, 23b is the sixth speed gear pair, the fourth forward transmission gear pair 24a, 24b is the first speed gear pair, the fifth forward transmission gear pair 25a, 25b is the third speed gear pair, The example in which the forward transmission gear pair 26a, 26b is assigned to the fourth speed gear pair has been described. However, the present invention is not limited to this, and the forward transmission gear pair at any position in FIGS. It is optional whether to assign a gear pair of speed.

  Further, in the above-described embodiment, the transmission 11 is arranged in series on the rear side in the axial direction of the engine 10 and is integrally connected to each other, and in this way, the engine 10 and the transmission that tend to increase in overall length. The increase in the length of the drive unit in which 11 is connected in series can be reduced.

  In the above-described embodiment, the fifth speed driving gear 22a and the third speed driving gear 25a and the sixth speed driving gear 23a and the fourth speed driving gear 26a are shared with each other. 22a and the third speed drive gear 25a, and the sixth speed drive gear 23a and the fourth speed drive gear 26a can be implemented so as not to be shared. The degree of freedom can be further increased.

It is a schematic diagram which shows the whole structure of one Embodiment of the transmission which has six sets of forward transmission gear pairs by this invention. It is a left view which shows arrangement | positioning of each axis | shaft and each gear which were seen from the axial direction of embodiment of the transmission shown in FIG. FIG. 6 is a side view of a drive unit in which a transmission having six forward transmission gear pairs according to the present invention is arranged and fixed in series on the rear side of an engine. It is a schematic diagram which shows the whole structure of the comparative example of the transmission which has 6 sets of forward transmission gear pairs.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Engine, 15 ... Input shaft, 16 ... First intermediate shaft, 17 ... Second intermediate shaft, 18 ... Reverse shaft, 19 ... Output shaft, 20A ... First gear transmission mechanism, 20B ... Second gear transmission mechanism, 20C ... reverse gear transmission mechanism, 21a, 21b ... first forward transmission gear pair, 22a, 22b ... second forward transmission gear pair, 23a, 23b ... third forward transmission gear pair, 24a, 24b ... fourth forward Transmission gear pair, 25a, 25b ... fifth forward transmission gear pair, 26a, 26b ... sixth forward transmission gear pair, 27 ... reverse gear train, 27a ... drive gear, 27b ... idle gear, 27c ... driven gear, 30A ... 1st switching clutch, 30B ... 2nd switching clutch, 30C ... 3rd switching clutch, 30D ... 4th switching clutch, 30E ... Reverse switching clutch.

Claims (5)

An input shaft that is rotationally driven by an engine, an output shaft that is connected to a drive wheel, a first intermediate shaft and a second intermediate shaft that are arranged in parallel to the input shaft and are respectively connected to the output shaft, and the input A first gear transmission mechanism provided between the shaft and the first intermediate shaft and including a plurality of gear pairs and a switching clutch; and a plurality of gear pairs and a switching clutch provided between the input shaft and the second intermediate shaft. In a transmission having six forward transmission gear pairs provided with a second gear transmission mechanism,
The first gear transmission mechanism is provided on one side of the first to third forward transmission gear pairs and the first forward transmission gear pair provided between the input shaft and the first intermediate shaft. A first switching clutch that switches power transmission between the input shaft and the first intermediate shaft by the forward transmission gear pair, and the two forward transmission gear pairs provided between the second and third forward transmission gear pairs. Comprising a second switching clutch for switching power transmission between the input shaft and the first intermediate shaft by
The second gear transmission mechanism is provided on one side of the fourth to sixth forward transmission gear pairs and the fourth forward transmission gear pair provided between the input shaft and the second intermediate shaft. The two forward transmission gear pairs are provided between a third switching clutch for switching power transmission between the input shaft and the second intermediate shaft by the forward transmission gear pair, and the fifth and sixth forward transmission gear pairs. Comprising a fourth switching clutch for switching the power transmission between the input shaft and the second intermediate shaft by
The first switching clutch and the fourth forward transmission gear pair, the third switching clutch and the first forward transmission gear pair, and the second switching clutch and the fourth switching clutch are respectively axes of the input shaft. 6. A transmission having six forward transmission gear pairs, wherein the transmission gear pairs are arranged so as to correspond to each other in the direction.   The transmission having the six forward transmission gear pairs according to claim 1, wherein the reverse shaft is arranged in parallel with the input shaft and connected to the output shaft, the input shaft, the second intermediate shaft, and the reverse shaft. And a reverse gear transmission mechanism including a reverse gear train including a drive gear, a free-wheeling gear, and a driven gear, and a reverse switching clutch. The driven gear is rotatably provided on the reverse shaft and is configured to rotate the reverse gear. 6 sets characterized in that the drive gear and the idle gear are shared with the first forward transmission gear pair or the fourth forward transmission gear pair so as to be detachable by a switching clutch. A transmission having a forward transmission gear pair.   3. The transmission having six forward transmission gear pairs according to claim 2, wherein the first forward transmission gear pair or the fourth forward transmission gear pair is a second speed gear pair or a first speed gear pair. A transmission having six pairs of forward transmission gears.   4. The transmission having six forward transmission gear pairs according to claim 2 or claim 3, wherein the first forward transmission gear pair or the fourth forward transmission gear pair is more than the remaining forward transmission gear pairs. A transmission having six pairs of forward transmission gears arranged on the engine side.   5. The transmission having six forward transmission gear pairs according to claim 1, wherein the transmission is arranged in series with the engine and integrally connected to each other. A transmission having six forward transmission gear pairs.

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