JP5856939B2 - Vehicle transmission - Google Patents

Description

  The present invention relates to a vehicle transmission.

  2. Description of the Related Art Conventionally, among continuously meshing gear transmissions, there is one in which a plurality of main shafts are arranged coaxially and one main shaft (inner shaft) is inserted through the other main shaft (outer shaft) so as to be relatively rotatable ( For example, see Patent Document 1).

JP 2011-208766 A

In the above configuration, it is considered that a washer for receiving the axial load of the outer shaft and for axial positioning of the outer shaft is sandwiched between the end of the outer spline formed on the inner shaft and the end of the outer shaft. It is done.
By the way, the washer receives the axial load of the outer shaft on one side and abuts the end of the outer spline having poor slidability on the other side. Therefore, the washer rotates relative to the inner shaft under an excessive axial load. If this occurs, it will cause washer wear.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to suppress wear of a washer that restricts axial movement of an outer shaft in a vehicular transmission that forms an axis of rotation with an inner shaft and an outer shaft that can rotate relative to each other.

As a means for solving the above problems, the invention described in claim 1 is directed to an inner shaft (47) and an outer shaft (48) in which a rotating shaft (47A) supporting a plurality of gears can be rotated relative to each other by a bearing (52). And a washer (10, 110, 210) for restricting axial movement of the outer shaft (48) adjacent to the bearing (52) supporting one end of the outer shaft (48). Further, in the vehicle gear transmission (40) that is always meshed , an outer spline (57) is formed in a portion adjacent to one end of the outer shaft (48) in the inner shaft (47) in the axial direction, said washer (10, 110, 210) has an end face (48a of the end face of said outer spline (57) (57c, 57e) and said outer shaft (48) And in conjunction with the positioning of the axial direction, and having said engagement portion integrally rotatably engaged with the inner shaft (47) (12, 112, 212).
The outer spline invention as set forth in claim 2, which transmits the to the surface of the inner shaft (47), a driving force in mesh with the internal splines of the slidable gear out axis direction of the plurality of gears (57) There is formed, said washer (10, 110, 210) is characterized by being arranged to abut axially the outer spline (57).
According to a third aspect of the present invention, the meshing portion (12) of the washer (10) projects in the axial direction on one side surface (11a) and engages with the outer spline (57). ).
The invention described in claim 4 is characterized in that a recess (13) is formed around the base of the axial protrusion (12).
According to a fifth aspect of the present invention, a stepped portion (57d) is formed at the end portion of the outer spline (57) by cutting off the top side of the tooth portion (57b) in a predetermined range in the axial direction, and the washer ( 110) meshing part (112) is an inner peripheral side projecting part (112) projecting radially inward and engaging with stepped part (57d) of outer spline (57), and washer (110) One side surface (111a) of the outer surface is in contact with the step surface (57e) of the stepped portion (57d) of the outer spline (57).
According to a sixth aspect of the present invention, the washer (210) is axially formed between the end surface (57c) of the tooth portion (57b) of the outer spline (57) and the end surface (48a) of the outer shaft (48). together are sandwiched, wherein the engagement portion of the washer (210) (212) is a washer-side notch portion formed on the inner circumferential side (212), the outer periphery of said inner shaft (47), said washer A shaft-side notch (58a) facing the side notch (212) is formed, and an engagement pin is formed in a space formed by the washer-side notch (212) and the shaft-side notch (58a). (213) is inserted.
According to the seventh aspect of the present invention, an outer peripheral stepped portion covering an outer periphery of the washer (10, 110, 210) is provided at an end of the outer shaft (48) on the washer (10, 110, 210) side. 48c), and the washer (10, 110, 210) abuts against the step surface (48a) of the outer peripheral side step portion (48c).
The invention described in claim 8 is provided with a pair of clutches (61, 62) for individually switching connection and disconnection of the driving force to each end of the inner shaft (47) and the outer shaft (48), The pair of clutches (61, 62) are characterized by being arranged at the ends of the inner shaft (47) and the outer shaft (48) in the same direction.

According to the first aspect of the present invention, in the transmission in which the inner shaft and the outer shaft are coaxially arranged so as to rotate relative to each other via the bearing, the washer for restricting the axial movement of the outer shaft is integrated with the inner shaft. Since the meshing portion that is rotatably engaged is provided, wear of the washer surface and the inner diameter can be suppressed without causing relative rotation between the inner shaft and the washer.
According to the second aspect of the present invention, in the structure in which the outer spline on the inner shaft surface and the washer are adjacent to each other, the washer and the inner shaft rotate integrally through the meshing portion, so that the washer is thrust from the outer shaft. Even if the load is pressed against the outer spline, wear of the washer can be suppressed.
According to the third aspect of the present invention, the washer and the inner shaft rotate integrally, and the washer and the inner shaft rotate together, so that the wear of the washer can be suppressed. Also, when assembling the transmission, if the axial projecting portion is not engaged with the outer spline, the outer shaft will shift from the original position in the axial direction and will not fit in the specified position. The operator can be informed.
According to the invention described in claim 4, since the fillet is eliminated at the base of the axial protrusion, when the washer is brought into contact with the end surface of the outer spline, one side surface of the washer is brought into contact with the end surface of the outer spline evenly. The thrust load can be received evenly.
According to the fifth aspect of the present invention, the stepped portion is formed at the end portion of the outer spline, and the washer is formed with the inner peripheral protruding portion that engages with the stepped portion of the outer spline. Since the inner shaft and the inner shaft rotate integrally, the wear of the washer can be suppressed. In addition, since the washer overlaps the axial range of the outer spline, it is possible to suppress the increase in the axial size of the transmission while increasing the thickness of the washer, thereby achieving both improvement in wear resistance and downsizing of the transmission. it can.
According to the sixth aspect of the present invention, the washer and the inner shaft rotate integrally with each other via the engaging pin, so that the wear of the washer can be suppressed.
According to the seventh aspect of the invention, the washer abuts against the step surface of the step portion on the outer peripheral side, thereby contributing to the axial positioning of the washer, and the meshing portion is engaged with the inner shaft when the transmission is assembled. When assembled in a state where they do not match, the washer hits the step surface of the step portion on the outer peripheral side, and the outer shaft is displaced in the axial direction from the original position and cannot be held in a predetermined position, so that an operator can be notified of an assembly error.
According to the eighth aspect of the present invention, in the twin clutch type transmission having the double-structure main shaft in which the relative rotation of the inner shaft and the outer shaft usually occurs, the pair of clutches are in the same direction of the inner shaft and the outer shaft. By gathering and arranging at the end of this, it is possible to enhance the effect of maintaining the axial position of the outer shaft by suppressing the wear of the washer.

It is sectional drawing which follows the crank-axis line of the power unit in 1st embodiment of this invention. It is a principal part enlarged view of the said sectional view. It is the front view which looked at the thrust washer shown in FIG. 2 from the left. It is IV-IV sectional drawing of FIG. It is sectional drawing equivalent to FIG. 2 in 2nd embodiment of this invention. It is a front view of the thrust washer shown in FIG. It is sectional drawing equivalent to FIG. 2 in 3rd embodiment of this invention. It is a front view of the thrust washer shown in FIG.

  Embodiments of the present invention will be described below with reference to the drawings.

<First embodiment>
FIG. 1 is a cross-sectional view taken along a crank axis C1 of a power unit P including an engine (internal combustion engine) E and a transmission M used for a motor of a motorcycle, for example.
The engine E includes a crankcase 26 that houses a crankshaft 25 having a crank axis (rotation center axis) C1 along the vehicle width direction (left-right direction), a cylinder body 27 that stands on the upper front side of the crankcase 26, a cylinder The cylinder head 28 is coupled to the upper end of the main body 27, and the head cover 29 is attached to the upper end of the cylinder head 28.
Pistons 34 corresponding to a plurality of cylinders are fitted in the cylinder body 27. Each piston 34 is connected to the crankshaft 25 via a connecting rod 34a. A generator cover 35 that covers a generator 37 is attached to the left side front portion of the crankcase 26. A clutch cover 45 that forms a clutch chamber 46 is attached to the right side surface of the crankcase 26. The arrow LH in the figure indicates the left side.

  The transmission M is accommodated in the rear portion of the crankcase 26. The transmission M includes a main shaft 47A having a main axis (rotation center axis) C2 parallel to the crank axis C1, a counter shaft 49 having a counter axis (rotation center axis) C3 parallel to the main axis C2, and a main shaft 47A. A plurality of gear trains (for example, first to sixth gear trains G1 to G6) that can be selectively established with the countershaft 49. The transmission M constitutes a twin clutch type transmission 40 together with a twin clutch 41 described later.

The main shaft 47A has a double structure including a first main shaft 47 on the inner peripheral side and a second main shaft 48 on the outer peripheral side.
The first main shaft 47 has a length over the entire length of the main shaft 47A. The second main shaft 48 has a length that extends only to the intermediate portion of the first main shaft 47. The second main shaft 48 is fitted on the outer periphery of the first main shaft 47 so as to be coaxial and relatively rotatable.
The first main shaft 47 is connected to the counter shaft 49 via a first speed gear train G1, a third speed gear train G3, and a fifth speed gear train G5. The second main shaft 48 is connected to the counter shaft 49 via the second speed gear train G2, the fourth speed gear train G4, and the sixth speed gear train G6.

  An intermediate portion of the first main shaft 47 and a right end portion of the second main shaft 48 penetrate the right side wall of the crankcase 26 and are rotatably supported by the right side wall via a ball bearing 51. The left end portion of the first main shaft 47 is rotatably supported on the left side wall of the crankcase 26 via a ball bearing 50. The right side portion of the first main shaft 47 protrudes into the clutch chamber 46, and the twin clutch 41 is supported on the right side portion. The right end portion of the first main shaft 47 is rotatably supported by the clutch cover 45 via a bearing (not shown). A plurality of needle bearings 52 are interposed between the first and second main shafts 47 and 48.

  The left end portion of the counter shaft 49 is rotatably supported on the left side wall of the crankcase 26 via a ball bearing 53. A right end portion of the counter shaft 49 is rotatably supported on the right side wall of the crankcase 26 via a ball bearing 55. The left end portion of the countershaft 49 protrudes to the left of the left side wall of the crankcase 26 (outside the crankcase 26), and a drive sprocket 56 of a chain transmission mechanism between the power unit P and the drive wheels is projected to the left end portion of the countershaft 49. Are supported so as to be integrally rotatable.

The twin clutch 41 is interposed between the first hydraulic clutch 61 interposed between the primary driven gear 68 and the first main shaft 47 of the primary reduction gear 60, and between the primary driven gear 68 and the second main shaft 48. The second hydraulic clutch 62 is coaxial. Reference numeral 67 in the drawing indicates a primary drive gear of the primary reduction gear 60.
A cylindrical transmission cylinder shaft 65 adjacent to the right of the right end of the second main shaft 48 is fitted on the right side of the first main shaft 47 so as to be relatively rotatable. A primary driven gear 68 is supported on the outer periphery of the intermediate portion of the transmission cylinder shaft 65 so as to be integrally rotatable.

A first clutch outer 80 of the first hydraulic clutch 61 is supported on the right side portion of the transmission cylinder shaft 65 so as to be integrally rotatable. A second clutch outer 90 of the second hydraulic clutch 62 is supported on the left side portion of the transmission cylinder shaft 65 so as to be relatively rotatable.
A first clutch inner 81 of the first hydraulic clutch 61 is supported on the right end portion of the first main shaft 47 so as to be integrally rotatable. An inner clutch plate is supported on the outer periphery of the first clutch inner 81, and an outer clutch plate is supported on the inner periphery of the first clutch outer 80 so as to be integrally rotatable. The clutch plate group 82 is pinched and frictionally engaged in the axial direction, so that the first hydraulic clutch 61 is engaged so that power can be transmitted, and the frictional engagement due to the pinching pressure is released. The one hydraulic clutch 61 enters a disconnected state in which power cannot be transmitted.

  A second clutch inner 91 of the second hydraulic clutch 62 is supported on the right end portion of the second main shaft 48 so as to be integrally rotatable. An inner clutch plate is supported on the outer periphery of the second clutch inner 91, and an outer clutch plate is supported on the inner periphery of the second clutch outer 90 so as to be integrally rotatable. When the clutch plate group 92 is pinched in the axial direction and frictionally engaged, the second hydraulic clutch 62 is in a connected state capable of transmitting power, and the frictional engagement due to the pinching pressure is released. The hydraulic clutch 62 enters a disconnected state where power cannot be transmitted.

  Then, one of the first hydraulic clutch 61 and the second hydraulic clutch 62 is connected and the other is disconnected, so that one of the gear trains connected to one of the first main shaft 47 and the second main shaft 48 is used. Power transmission can be performed. At this time, the gear train connected to the other of the first main shaft 47 and the second main shaft 48 is selected in advance, and from this state, the first hydraulic clutch 61 and the second hydraulic clutch 62 are selected. By disconnecting one and connecting the other, the transmission is switched to power transmission using the previously selected gear train, and the transmission M is shifted up or down.

  The transmission M is of a constant meshing type in which the driving gear and the driven gear corresponding to each gear are always meshed. Each gear includes a free gear that is rotatable relative to the corresponding shaft and a slide gear (shifter) that is spline-fitted to the corresponding shaft. One of the free gear and the slide gear is provided with an axially convex dog, and the other is provided with an axially concave slot to engage the dog. Then, an arbitrary slide gear is slid by a change mechanism (not shown) to engage the dog and the slot, thereby switching to power transmission using a gear train corresponding to one of the gear positions.

  As shown in FIG. 2, an outer spline 57 is formed on the outer periphery of the left side of the first main shaft 47 so that, for example, a shifter S1 integrated with the drive gear G3D of the third speed gear train G3 is fitted. On the right side of the outer spline 57, a flat shaft portion 58 for fitting the second main shaft 48 is connected. The right end portion of the outer spline 57 and the left end portion of the second main shaft 48 are adjacent to each other via an annular thrust washer 10 that is externally fitted to the first main shaft 47. Hereinafter, a direction along the main axis C2 is referred to as an axial direction, a direction orthogonal to the main axis C2 is referred to as a radial direction, and a circumferential direction around the main axis C2 is referred to as a circumferential direction.

  Referring also to FIG. 3, an outer peripheral side stepped portion 48 c that expands the inner peripheral surface in a stepped shape is formed on the inner periphery of the left end portion of the second main shaft 48. The thrust washer 10 is fitted on the flat shaft portion 58 of the first main shaft 47, and the right end surface 57c of the tooth portion 57b of the outer spline 57 and the inner left end surface 48a of the outer peripheral side stepped portion 48c of the second main shaft 48 are connected to the right end surface 48a. An annular washer main body 11 sandwiched in the axial direction and a left side surface 11a on the outer spline 57 side of the washer main body 11 protruding leftward in the axial direction, and a part of the plurality of groove portions 57a (for example, the circumference) of the outer spline 57 A plurality of axially projecting portions 12 engaged with the right end portion of the four positions arranged in every 90 degrees in a direction so as to be integrally rotatable. The code | symbol 13 in the figure shows the waste part formed in the circumferential direction both sides of each axial direction protrusion part 12 in the left side surface 11a of the washer main body 11 (refer FIG. 4).

  The washer body 11 has the inner peripheral side of the left side surface 11 a in contact with the right end surface 57 c of the tooth portion 57 b of the outer spline 57, and the outer peripheral side of the right side surface 11 b is the inner left end of the outer peripheral side stepped portion 48 c of the second main shaft 48. Contact the surface 48a. A needle bearing 52 between the first main shaft 47 and the second main shaft 48 is adjacent to the inner peripheral side of the right side surface 11 b of the washer body 11.

  The washer body 11 of the thrust washer 10 enters the outer peripheral side stepped portion 48c of the second main shaft 48 in the axial direction. The axial protrusion 12 of the thrust washer 10 protrudes to the left of the left end surface 48 b of the second main shaft 48 and engages with the right end of the groove 57 a of the outer spline 57. The left end surface of the axial protrusion 12 is separated to the right of the shifter S1 (see FIG. 2) that has moved rightward on the outer spline 57. The shifter S2 (see FIG. 2) that has moved to the left on the left end surface 48b of the second main shaft 48 and the outer spline 59 of the second main shaft 48 is also separated to the right of the shifter S1 that has moved to the right. To do. Reference numeral G4D in the figure indicates a drive gear of, for example, a fourth speed gear train G4 integrated with the shifter S2.

  In such a configuration, when the first main shaft 47 and the second main shaft 48 rotate relative to each other, the plurality of axial protrusions 12 engage with the right end of the groove 57a of the outer spline 57 so as to be integrally rotatable. The washer 10 rotates integrally with the first main shaft 47. That is, since the thrust washer 10 does not rotate with respect to the outer spline 57, even when a burr is generated at the right end portion of the outer spline 57, wear of the left side surface 11a in contact with the outer spline 57 of the thrust washer 10 is suppressed. It is done.

  Further, when the plurality of axial protrusions 12 are not fitted in the grooves 57a of the outer spline 57 due to a shift in the circumferential position of the thrust washer 10 or the like, the second height is equal to the axial height of the axial protrusion 12. The main shaft 48 is displaced to the right. At this time, since the main shaft 47A cannot be assembled into the crankcase 26, it is prevented that the assembly of the main shaft 47A is completed while the assembly of the thrust washer 10 is incomplete. Similarly, even when the thrust washer 10 is assembled upside down (with the axially protruding portion 12 facing right), the assembly of the main shaft 47A is prevented from being completed while the thrust washer 10 is misassembled. Is done.

  As described above, the double rotary shaft structure in the above embodiment has the first main shaft 47 in which the outer spline 57 is formed and the flat shaft portion 58 that is adjacent to the outer spline 57 in the axial direction. A thrust washer 10 that is externally fitted to the first main shaft 47 and sandwiched between an end portion of the outer spline 57 and an end portion of the second main shaft 48. The thrust washer 10 is engaged with the first main shaft 47 so as to be integrally rotatable, so that the thrust washer 10 is placed between the end of the outer spline 57 of the first main shaft 47 and the end of the second main shaft 48. The thrust washer 10 can be rotated integrally with the first main shaft 47 (outer spline 57) while being sandwiched between the outer Wear is suppressed in the thrust washer 10 by the relative rotation of the line 57, it is possible to suppress the generation of mechanical noise due to the axial backlash of the second main shaft 48.

  The double rotating shaft structure has an axial direction in which the thrust washer 10 protrudes in the axial direction from the annular washer body 11 and the surface of the washer body 11 on the outer spline 57 side and engages with the end of the outer spline 57. And the thrust washer 10 can be rotated integrally with the first main shaft 47 via the axial projection 12 and the circumferential position of the axial projection 12 is shifted to form an outer spline. When the thrust washer 10 is not engaged with the end portion 57 or the thrust washer 10 is installed upside down, the axial position of the second main shaft 48 is shifted by the height of the axial projection 12, so that the thrust washer Ten assembly failures can be detected.

  In the double rotation shaft structure, the first main shaft 47 and the second main shaft 48 constitute a double-structure main shaft 47A of the twin clutch transmission 40, whereby the first main shaft 47 of the main shaft 47A. In the twin clutch transmission 40 in which the relative rotation of the second main shaft 48 normally occurs, wear of the thrust washer 10 can be suppressed.

<Second embodiment>
Next, a second embodiment of the present invention will be described with reference to FIGS.
This embodiment is different from the first embodiment in that a cut portion 57d is formed by cutting the top side of the tooth portion 57b at the right end of the outer spline 57 of the first main shaft 47, and this cut portion 57d. The thrust washer 110 is sandwiched between the step-like second right end surface 57e formed at the left end of the shaft and the inner left end surface 48a of the second main shaft 48, and the inner peripheral side formed on the inner peripheral side of the thrust washer 110 This is particularly different in that the protrusion 112 is engaged with the groove 57a of the outer spline 57 remaining in the cut portion 57d. The other components that are the same as those in the above embodiment are given the same reference numerals, and detailed description thereof is omitted.

  The thrust washer 110 includes an annular washer main body 111 that is fitted over the left end portion of the flat shaft portion 58 of the first main shaft 47 and the cutout portion 57d formed on the outer periphery of the right end portion of the outer spline 57, and the washer main body 111. Projecting inward in the radial direction from the inner peripheral surface of the outer peripheral portion of the outer spline 57 remaining in the cut portion 57d and engaged with a part of the plurality of groove portions 57a (for example, four locations arranged every 90 degrees in the circumferential direction) so as to be integrally rotatable. A plurality of inner peripheral side protruding portions 112 and a left side surface 111a as a contact portion that contacts the second right end surface 57e of the outer spline 57 from the right side.

  The cut portion 57d is formed so as to cut the top side of the tooth portion 57b to about half the height. A second right end surface 57e orthogonal to the axial direction is formed in a step shape at the left end of the cutout 57d. The washer body 111 is sandwiched between the second right end surface 57e of the first main shaft 47 and the inner left end surface 48a of the second main shaft 48 in the axial direction. The washer body 111 has a thickness equivalent to the height from the right side surface 111b of the washer body 111 to the top of the axial protrusion 12 in the thrust washer 10 of the first embodiment.

  In such a configuration, when the first main shaft 47 and the second main shaft 48 are rotated relative to each other, the plurality of inner peripheral side protruding portions 112 are engaged with the right end portion of the groove portion 57a of the outer spline 57 so as to be integrally rotatable, The thrust washer 110 rotates integrally with the first main shaft 47. That is, since the thrust washer 110 does not rotate with respect to the outer spline 57, similarly to the first embodiment, wear on the outer spline 57 side of the thrust washer 110 is suppressed.

  As described above, in the double rotating shaft structure in the above embodiment, the outer spline 57 has the cutout portion 57d that cuts out the top side of the tooth portion 57b at the end portion on the thrust washer 110 side, and the thrust washer 110 is An annular washer main body 111, an inner peripheral protrusion 112 that protrudes radially inward from the inner peripheral side of the washer main body 111 and engages with a groove 57a of the outer spline 57 remaining in the cut part 57d, and a shaft at the cut part 57d The thrust washer 110 between the second right end surface 57e of the first main shaft 47 and the second main shaft 48 by having a contact portion (left side surface 111a) that contacts the second right end surface 57e intersecting the direction. The thrust washer 110 can be rotated integrally with the first main shaft 47 via the inner peripheral protruding portion 112 while being sandwiched between the left end surface 48a. Kill Therefore, wear of the thrust washer 110 by relative rotation of the outer spline 57 can be suppressed, it is possible to suppress the generation of mechanical noise due to the axial backlash of the second main shaft 48.

<Third embodiment>
Next, a third embodiment of the present invention will be described with reference to FIGS.
This embodiment is different from the first embodiment in that a thrust washer 210 having an axial protrusion 12 from the thrust washer 10 and a notch for engaging a knock pin 213 on the inner peripheral portion of the washer body 11 is provided. It is particularly different in terms of use. The other components that are the same as those in the above embodiment are given the same reference numerals, and detailed description thereof is omitted.

  The thrust washer 210 is a knock pin formed in the washer body 11 and a plurality of locations (two locations facing each other in the radial direction in FIG. 8) on the inner peripheral side of the washer body 11, and fixed to the fitting hole of the flat shaft portion 58. And a notch 212 for engaging with 213. The washer body 11 is sandwiched between the right end surface 57 c of the tooth portion 57 b of the outer spline 57 and the inner left end surface 48 a of the second main shaft 48 in the axial direction.

  In such a configuration, when the first main shaft 47 and the second main shaft 48 are rotated relative to each other, the plurality of knock pins 213 are engaged with the notch portion 212 so as to be integrally rotatable, so that the thrust washer 210 is engaged with the first main shaft 47. And rotate together. That is, since the thrust washer 210 does not rotate with respect to the outer spline 57, the wear on the outer spline 57 side of the thrust washer 210 is suppressed as in the first embodiment.

  As described above, in the double rotating shaft structure in the above embodiment, the thrust washer 210 has the notch portion 212 that engages with the knock pin 213 fixed to the first main shaft 47, so that the knock pin 213 and the notch are cut. Since the thrust washer 210 can be rotated integrally with the first main shaft 47 through the notch 212, the wear of the thrust washer 210 due to the relative rotation of the outer spline 57 is suppressed, and the backlash of the second main shaft 48 in the axial direction is suppressed. The generation of mechanical noise due to can be suppressed.

The present invention is not limited to the above embodiment, and may be applied to, for example, a parallel or V-type multi-cylinder engine or a single-cylinder engine. The present invention may be applied, may be applied to an engine having a single clutch, or may be applied to a rotating shaft other than a transmission.
And the structure in the said embodiment is an example of this invention, A various change is possible in the range which does not deviate from the summary of the said invention.

10, 110, 210 Thrust washer (washer)
11,111 Washer body 11a Left side (one side)
12 Axial protruding part (meshing part)
13 Nusumi part (concave part)
40 Twin clutch transmission (vehicle transmission)
47A Main shaft (rotary shaft)
47 First main shaft (inner shaft)
48 Second main shaft (outer shaft)
48a Inner left end surface (step surface)
48c Outer peripheral side step 52 Needle bearing (bearing)
57 Outer spline 57a Groove part 57b Tooth part 57d Cut part (stepped part)
57e Second right end face (step surface)
58 Flat shaft 58a Pin hole (shaft side notch)
61 First hydraulic clutch (clutch)
62 Second hydraulic clutch (clutch)
111a Left side (one side)
112 Inner peripheral side protruding part (meshing part)
212 Notch (meshing part, washer side notch)
213 Knock pin (engagement pin)

Claims (8)

A rotating shaft (47A) that supports a plurality of gears is formed by an inner shaft (47) and an outer shaft (48) that can rotate relative to each other by a bearing (52), and supports one end of the outer shaft (48). An always-meshing vehicle transmission (40) provided with washers (10, 110, 210) for restricting axial movement of the outer shaft (48) adjacent to the bearing (52). ,
An outer spline (57) is formed in a portion of the inner shaft (47) adjacent to the one end of the outer shaft (48) in the axial direction,
The washer (10, 110, 210) is axially positioned by the end surface (57c, 57e) of the outer spline (57) and the end surface (48a) of the outer shaft (48), and the inner shaft ( 47) A vehicular transmission having a meshing portion (12, 112, 212) that engages with 47) so as to be integrally rotatable. Wherein the surface of the inner shaft (47), the outer spline for transmitting a driving force mesh with the internal splines of the slidable gear out axis direction of the plurality of gears (57) are formed,
Said washer (10, 110, 210) for a vehicle transmission according to claim 1, characterized in that it is arranged to abut axially the outer spline (57).   The meshing part (12) of the washer (10) is an axial projecting part (12) that projects in the axial direction on one side surface (11a) and engages with the outer spline (57). The vehicular transmission according to claim 2.   The vehicular transmission according to claim 3, wherein a recess (13) is formed around a base of the axial protrusion (12). At the end of the outer spline (57), a stepped portion (57d) is formed by cutting off the top side of the tooth portion (57b) in a predetermined range in the axial direction.
The meshing portion (112) of the washer (110) is an inner peripheral protruding portion (112) that protrudes inward in the radial direction and engages with the stepped portion (57d) of the outer spline (57).
The vehicle transmission according to claim 2, wherein one side surface (111a) of the washer (110) abuts on a step surface (57e) of a stepped portion (57d) of the outer spline (57). . The washer (210) is sandwiched in the axial direction between the end surface (57c) of the tooth portion (57b) of the outer spline (57) and the end surface (48a) of the outer shaft (48), and the washer (210) The meshing portion (212) is a washer-side cutout portion (212) formed on the inner peripheral side,
On the outer peripheral side of the inner shaft (47), a shaft side notch (58a) facing the washer side notch (212) is formed,
The vehicle transmission according to claim 2, wherein an engagement pin (213) is inserted into a space formed by the washer-side notch (212) and the shaft-side notch (58a). .   An outer step portion (48c) covering the outer periphery of the washer (10, 110, 210) is provided at an end of the outer shaft (48) on the washer (10, 110, 210) side, and the outer peripheral side The vehicular transmission according to any one of claims 1 to 6, wherein the washer (10, 110, 210) abuts on a step surface (48a) of the step portion (48c). A pair of clutches (61, 62) for individually switching connection and disconnection of the driving force to each end of the inner shaft (47) and the outer shaft (48) are provided,
The pair of clutches (61, 62) are arranged in a concentrated manner at ends of the inner shaft (47) and the outer shaft (48) in the same direction. The transmission for a vehicle according to the item.

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