JP7268525B2 - Transmission lubrication structure - Google Patents

Description

The present invention relates to a lubrication structure for a transmission.

The transmission of Patent Document 1 includes a transmission case configured to store oil, and an input shaft, a counter shaft, and an output shaft rotatably supported by the transmission case. A plurality of transmission gears are coaxially provided on the counter shaft, and the transmission gears are configured to be at least partially immersed in oil stored in the transmission case.

JP 2019-44897 A

In this conventional transmission lubrication structure, when the transmission gear rotates, the oil stored in the bottom portion of the transmission case is agitated, thereby generating agitation resistance and reducing fuel consumption. On the other hand, if the oil level in the transmission case is lowered in order to improve fuel efficiency, the transmission gears may not be immersed in the oil. In this case, lubrication of the transmission gear tends to be insufficient.

SUMMARY OF THE INVENTION The present invention provides a lubrication structure for a transmission that can reduce the oil level and improve fuel efficiency while ensuring the amount of oil supplied to members to be lubricated.

In order to solve the above problems, the present invention is characterized by the following configuration.

The present invention
a transmission case that accommodates a member to be lubricated;
an oil supply member having an oil path that guides oil to the member to be lubricated,
A lubricating structure for a transmission is provided, wherein the oil supply member is provided with an oil recovery portion that connects the inner surface of the transmission case and the oil path.

According to this configuration, the oil flowing along the inner surface of the transmission case is collected by the oil collecting portion, flows into the oil path, and then is supplied to the member to be lubricated. can be supplied to As a result, since a small amount of oil can efficiently lubricate the members to be lubricated, the oil level in the transmission case can be lowered.

In addition, when the oil level in the transmission case is lowered, the amount of oil stirred by the rotation of the transmission gears is reduced, so the resistance to stirring is reduced and the fuel consumption can be improved.

A guide portion may be formed in the transmission case to guide oil to the oil recovery portion.

According to this configuration, since the transmission case is formed with the guide portion that guides the oil to the oil recovery portion, the oil traveling along the inner surface of the transmission case can be efficiently recovered by the oil recovery portion.

The oil recovery portion may include a first end surface located outside the transmission case relative to the inner surface of the transmission case.

According to this configuration, the first end face located outside the transmission case relative to the inner surface of the transmission case allows the oil collecting portion to reliably collect the oil that runs along the inner surface of the transmission case.

The oil recovery portion may include a second end surface facing the first end surface inside the transmission case with respect to the first end surface.

The member to be lubricated may be a reduction gear of an output reduction type transmission.

According to the lubricating structure of the transmission according to the present invention, it is possible to reduce the oil level and improve fuel efficiency while ensuring the amount of oil supplied to the members to be lubricated.

1 is a longitudinal sectional view of a transmission according to an embodiment of the invention; FIG. Sectional drawing in the II-II line of FIG. FIG. 2 is a cross-sectional perspective view of a speed reduction drive gear and a speed reduction driven gear and its surroundings; The figure which looked at the periphery of an oil supply member from the front. FIG. 3 is a perspective view of an oil supply member; FIG. 4 is a top view of the oil supply member; Sectional drawing in the VII-VII line of FIG. Sectional drawing in the VIII-VIII line of FIG. FIG. 4 is a cross-sectional perspective view for explaining a mounting structure of the oil supply member to the gear case;

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. It should be noted that the following description is essentially merely an example, and is not intended to limit the present invention, its applications, or its uses. Moreover, the drawings are schematic, and the ratio of each distance is different from the actual one.

FIG. 1 is a longitudinal sectional view of a manual transmission 1 to which a lubricating structure according to one embodiment of the invention is applied. The manual transmission 1 is arranged vertically in the vehicle such that the axis of the transmission shaft is oriented in the longitudinal direction of the vehicle. In the following description, the front-rear, left-right, and vertical directions of the manual transmission 1 correspond to the front-rear, left-right, and vertical directions of the vehicle on which the manual transmission 1 is mounted.

The manual transmission 1 has a transmission case 2 and a gear train 10 housed in the transmission case 2 . The transmission case 2 includes a clutch housing 3 connected to the rear surface of a power source (for example, an engine) (not shown) and a gear case 4 connected to the rear side thereof. A bearing housing 60 that is formed separately from the gear case 4 and extends in a direction orthogonal to the front-rear direction is fixed to the inner rear portion of the gear case 4 .

The gear train 10 includes a main shaft 11 as a speed change shaft and a counter shaft 14 arranged substantially directly below and in parallel with the main shaft 11 . The main shaft 11 and the counter shaft 14 extend in the front-rear direction and are rotatably supported by the transmission case 2 . The main shaft 11 has an input shaft 12 that is detachably connected to an output shaft (not shown) of a power source, and an output shaft 13 arranged on the same axis on the rear side of the input shaft 12 .

The front portion of the input shaft 12 is rotatably supported by the clutch housing 3 via a first bearing 21 . The front portion of the output shaft 13 is rotatably supported by the bearing housing 60 via the second bearing 22 , and the rear portion of the output shaft 13 is rotatably supported by the bearing support wall 70 of the gear case 4 via the third bearing 23 . supported by The rear portion of the input shaft 12 is rotatably supported in a fitting hole formed in the front end portion of the output shaft 13 via, for example, a needle bearing. The third bearing 23 of the present embodiment is a sealed bearing in which grease or lubricating oil is enclosed.

The front portion of the counter shaft 14 is rotatably supported by the clutch housing 3 via a fourth bearing 24 , and the rear portion of the counter shaft 14 is rotatably supported by a bearing support wall 70 of the gear case 4 via a fifth bearing 25 . A middle portion located on the rear side between the front portion and the rear portion is rotatably supported with respect to the bearing housing 60 via the sixth bearing 26 .

The input shaft 12 is provided with a plurality of input gears 30 including a reverse speed drive gear 37 and first to fifth drive gears 31 to 35 in order from the front. The counter shaft 14 is provided with a plurality of transmission gears 40 including a reverse driven gear 47, first to fifth driven gears 41 to 45, and a reduction drive gear 48 in order from the front. A reduction driven gear 38 is provided on the output shaft 13 .

The reduction drive gear 48 and the reduction driven gear 38 are helical gears. The width (lengthwise dimension) of the reduction drive gear 48 and the reduction driven gear 38 is larger than the width (lengthwise dimension) of the first to fifth drive gears 31 to 35 and the first to fifth driven gears 41 to 45. big. The reduction drive gear 48 according to the present embodiment is an example of a member to be lubricated according to the invention.

Between the input shaft 12 and the counter shaft 14, a constant-meshing gear train G1, G2, G3 is provided by a plurality of input gears 30 and a plurality of transmission gears 40 (excluding the reduction drive gear 48). , G4, G5 and GR are constructed. Between the output shaft 13 and the counter shaft 14, a reduction driven gear 38 and a reduction drive gear 48 form a constant mesh reduction gear train G0.

Specifically, between the input shaft 12 and the counter shaft 14, a reverse speed gear train GR, a first speed gear train G1, a second speed gear train G2, a third speed gear train G3, A fourth speed gear train G4 and a fifth speed gear train G5 are provided in order from the front. In the gear train 10, the sixth gear stage is configured as a direct coupling stage in which the rotation from the power source is transmitted from the input shaft 12 to the output shaft 13 at the same number of revolutions.

The first and second gear trains G1 and G2 are loosely fitted on the first and second drive gears 31 and 32 integrally formed on the outer periphery of the input shaft 12 and on the outer periphery of the counter shaft 14. It is composed of first and second driven gears 41 and 42 . The third to fifth gear trains G3 to G5 are spline-fitted to third to fifth drive gears 33 to 35 loosely fitted to the outer periphery of the input shaft 12 and to the outer periphery of the counter shaft 14. It is composed of third to fifth driven gears 43-45.

The reduction gear train G0 includes a reduction drive gear 48 spline-fitted to the outer circumference of the counter shaft 14 and a reduction driven gear 38 spline-fitted to the outer circumference of the output shaft 13 . The outer diameter of the reduction drive gear 48 is smaller than the outer diameter of the reduction driven gear 38. Therefore, the rotation transmitted to the counter shaft 14 is reduced at a predetermined gear ratio by the reduction gear train G0 to the output shaft 13. is transmitted to

Further, the input shaft 12 and the counter shaft 14 are provided with synchronizing devices 16 to 19 for connecting the drive gear or driven gear loosely fitted thereon to the respective shafts so as to be able to transmit power. Specifically, the input shaft 12 is provided with a third-fourth speed synchronizer 17 between the third and fourth drive gears 33 and 34 in the axial direction. A synchronizing device 18 for fifth and sixth speeds is provided between them in the axial direction.

A reverse speed synchronizing device 19 is provided adjacent to the front side of the reverse speed driven gear 47 loosely fitted on the counter shaft 14 , and is axially spaced between the first and second driven gears 41 and 42 . A synchronizer 16 for 1st-2nd speed is provided.

That is, except for the sixth speed, which is a direct-coupling speed, the drive torque input to the input shaft 12 from the power source is transmitted by any one of the synchronizing devices 16 to 19 to the first to fifth gears. The speed is changed at a predetermined gear ratio via either one of the speed gear trains G1 to G5 or the reverse speed gear train GR, is transmitted to the counter shaft 14, and is finally transmitted from the counter shaft 14 to the reduction gear train G0. and is transmitted to the output shaft 13. That is, the gear train 10 is configured as a so-called output reduction type in which the speed is reduced on the output shaft 13 side.

As shown in FIG. 1, the space S defined inside the gear case 4 includes a first space S1 defined on the front side including the bearing housing 60, and a stepped surface 4a on the rear side perpendicular to the front-rear direction. and a second space S2 that is vertically and horizontally reduced by one level. Further, the space S defined inside the gear case 4 includes a third space S3 defined behind the third bearing 23 . Specifically, the third space S3 is defined by the bearing support wall 70 of the gear case 4 into which the third bearing 23 and the fifth bearing 25 are press-fitted.

An oil storage portion 7 is formed in the inner lower portion of the transmission case 2, and the oil stored therein is hatched with two-dot chain lines. Oil for lubricating each part of the gear train 10 is stored in the oil reservoir 7 . The oil level L of the oil reservoir 7 is positioned above the lower ends of the plurality of transmission gears 40 (excluding the fifth driven gear 45 and the reduction drive gear 48) provided on the counter shaft 14. As shown in FIG. Therefore, the plurality of transmission gears 40 (excluding the fifth driven gear 45 and the reduction drive gear 48) are submerged in the oil reservoir 7 at their lower portions. On the other hand, the oil level L of the oil reservoir 7 in this embodiment is located below the lower end of the reduction drive gear 48 . Therefore, the lower portion of the reduction drive gear 48 is not submerged in the oil reservoir 7 .

An oil separator 51 is provided below the third to fifth driven gears 43-45. The oil separator 51 has a semicircular cross section that is open upward so as to cover substantially lower halves of the third to fifth driven gears 43 to 45 from below with a gap therebetween. It extends rearward to the front end face of the bearing housing 60 . Since the oil separator 51 reduces the amount of oil stirred by the third to fifth driven gears 43 to 45, the resistance to stirring by the transmission gear 40 is reduced.

An oil baffle 53 is provided on the sides of the first and second driven gears 41 and 42 . FIG. 2 is a cross-sectional view taken along line II--II of FIG. Referring also to FIG. 2, the oil baffle 53 is configured to cover the first and second driven gears 41 and 42 from the sides, and the outer peripheral teeth of the rotating first and second driven gears 41 and 42 is configured to guide the oil raked up from the oil storage portion 7 upward.

Specifically, in FIG. 2, the second drive gear 32 rotates clockwise (rotating direction R1), and the second driven gear 42 meshing with it rotates counterclockwise (rotating direction R2) in the opposite direction. , and the outer peripheral tooth portion moves upward in the area on the left side of the shaft center (on the right side in FIG. 2 as viewed from the front). The oil baffle 53 is configured to cover the left side of the second driven gear 42 from the left with a space therebetween. It extends upward and opens upward at its upper end.

An oil path 55 extending in the axial direction is provided above the input shaft 12 . The oil path 55 has a first passage 56 located above and a second passage 58 located on the left side of the first passage 56 at a position one step lower via a vertical wall portion 57 extending obliquely downward to the left from the left end of the passage. and

As shown in FIG. 1 , the first passage 56 extends in the longitudinal direction from above the second drive gear 32 to the front end surface of the bearing housing 60 . Also referring to FIG. 2 , the first passage 56 is formed to have an L-shaped cross section, and is raked up by the plurality of transmission gears 40 , especially the first and second driven gears 41 and 42 . It is configured to receive the oil guided upward and guide it rearward along the axial direction of the input shaft 12 . A plurality of oil holes 56a are formed through the first passage 56 in the vertical direction. are to be supplied.

As shown in FIG. 2 , the second passage 58 has a gutter shape (U-shaped cross section) with an open top, and oil or oil guided from the first passage 56 through the vertical wall portion 57 The oil raked up by the multiple speed change gears 40 is directly guided. 1, the second passage 58 extends rearward along the axial direction of the left side of the input shaft 12, passes through the left side of the bearing housing 60, and passes through the third bearing 23 side. has reached the department.

FIG. 3 is a cross-sectional perspective view showing the periphery of the reduction drive gear 48 and the reduction driven gear 38. As shown in FIG. Referring to FIG. 3, the second passageway 58 extends to the side of the third bearing 23, as previously described. Specifically, the second passage 58 is inserted through an insertion hole 71 formed in a bearing support wall 70 of the gear case 4 . The insertion hole 71 is provided on the side of the third bearing 23 and communicates the second space S2 and the third space S3 (shown in FIG. 1) inside the gear case 4 . Thus, oil is supplied to the third space S3 via the second passage 58. As shown in FIG. Therefore, the insertion hole 71 includes a second space S2 in the transmission case 2 in which the reduction drive gear 48 and the reduction driven gear 38 are arranged, and a transmission case in which the oil supplied from the second passage 58 is stored. It communicates with the third space S3 in 2.

As shown in FIG. 3, the second space S2 of the transmission case 2 is provided with an oil supply member 80 for supplying oil to the drive gear 48 for reduction. The oil supply member 80 of the present embodiment collects the oil running along the inner surface of the gear case 4 and supplies the collected oil to the reduction drive gear 48 . The oil supply member 80 is arranged between the bearing housing 60 and the bearing support wall 70 .

FIG. 4 is a front view of the periphery of the oil supply member 80. As shown in FIG. In FIG. 4, illustration of the reduction driven gear 38, the reduction drive gear 48, the third bearing 23, and the fifth bearing 25 is omitted. 3 and 4, the bearing support wall 70 of the gear case 4 is formed with a guide portion 72 for guiding oil to the oil supply member 80. As shown in FIG. The guide portion 72 is provided so as to extend from the insertion hole 71 of the bearing support wall 70 to the oil supply member 80 . The guide portion 72 is formed in a groove shape (U-shaped cross section) with an open front. Specifically, the guide portion 72 is formed by a rear end surface 70a of the bearing support wall 70 and a pair of side surfaces 70b and 70c that protrude forward from the rear end surface 70a and extend in the vertical direction. The side surface 70b is also provided with a top surface 70d located forward of the rear end surface 70a.

FIG. 5 is a perspective view of the oil supply member 80 alone according to this embodiment. FIG. 6 is a top view of the oil supply member 80 according to this embodiment. 7 is a cross-sectional view taken along line VII-VII of FIG. 6. FIG. 8 is a cross-sectional view taken along line VIII-VIII of FIG. 6. FIG. 6 and 8 show the rotation direction of the reduction drive gear 48 during forward movement.

5 and 6, the oil supply member 80 includes a main body portion 81, two front mounting portions 80a projecting forward from the main body portion 81, and a rear mounting portion 80a projecting rearward from the main body portion 81. and a mounting portion 80b.

A main body portion 81 of the oil supply member 80 includes an oil recovery portion 82, a first flow path portion 83 extending in the front-rear direction, a second flow path portion 84 extending in the left-right direction, and provided below the second flow path portion 84. and a second supply unit 85 .

The oil recovery portion 82 connects the inner surface of the transmission case 2 (gear case 4 ) and the first flow path portion 83 . Thus, the oil recovery portion 82 is configured to recover the oil running along the inner surface of the transmission case 2 (gear case 4 ) and flow it into the first flow path portion 83 . The oil collecting portion 82 has a first end surface 82a that is substantially circular in front view, a substantially semi-cylindrical bottom surface 82b that is provided forward and connected to the first end surface 82a, and is opposed to the first end surface 82a on the front side, It has a bottom surface 82b and a second end surface 82c provided in a row. A portion of the second end surface 82c extends above the upper end of the bottom surface 82b.

As shown in FIG. 7 , in the present embodiment, the first end surface 82 a of the oil recovery portion 82 is arranged rearward in the front-rear direction from the rear end surface 70 a of the bearing support wall 70 . In other words, the first end face 82a of the oil recovery portion 82 is located outside the transmission case 2 (gear case 4) relative to the bearing support wall 70. As shown in FIG. A first end surface 82a of the oil collecting portion 82 is formed integrally with the rear mounting portion 80b.

The second end face 82c of the oil recovery portion 82 is arranged on the front side in the front-rear direction of the oil recovery portion 82 relative to the first end face 82a.

As shown in FIG. 5, the first flow path portion 83 is configured in a gutter shape (U-shaped cross section) with an open top. As shown in FIG. 6, the first flow path portion 83 is connected to the oil recovery portion 82 and configured to guide the oil recovered by the oil recovery portion 82 from the rear side to the front side. Also referring to FIG. 7, with the oil supply member 80 attached to the transmission case 2 (shown in FIG. 1), the first flow path portion 83 extends obliquely downward from the rear side toward the front side. Inclined.

As shown in FIG. 5, the second flow path portion 84 is configured in a gutter shape (U-shaped cross section) with an open top. The second flow path portion 84 is connected to the front end of the first flow path portion 83 . As shown in FIG. 6, the second flow path portion 84 is configured to guide the oil guided from the rear side to the front side by the first flow path portion 83 from the left side to the right side. Also, referring to FIG. 8, the second flow path portion 84 is inclined downward from the left side to the right side.

As shown in FIG. 5, a first supply portion 84a is provided at the end portion of the second flow path portion 84 on the opposite side (right side) to the first flow path portion 83 in the left-right direction. Referring also to FIG. 6 , the first supply portion 84 a is provided so as to face the reduction drive gear 48 . In addition, the first supply portion 84a is provided at a position eccentric with respect to the center line CL of the reduction drive gear 48 in the axial direction (front-rear direction in this embodiment). In other words, the first supply portion 84a is arranged deviated from the center line CL of the reduction drive gear 48 in the front-rear direction. Specifically, the first supply portion 84a is arranged in front of the axial center line CL of the reduction drive gear 48 in the front-rear direction.

As shown in FIG. 6, the first supply portion 84a is arranged so as to overlap with the reduction drive gear 48 when viewed from above. That is, as shown in FIG. 8, the first supply portion 84a is positioned above the reduction drive gear 48. As shown in FIG. As a result, the oil discharged from the first supply portion 84a is supplied to the reduction drive gear 48 from above.

As shown in FIG. 5, a plate-like downwardly extending portion 84b extending downward is provided at the end of the second flow path portion 84 on the opposite side (right side) of the first flow path portion 83 in the left-right direction. there is In other words, the downward extension portion 84b is provided to extend downward from the first supply portion 84a. In addition, as shown in FIG. 6, the downwardly extending portion 84b is arranged so as to overlap with the reduction drive gear 48 when viewed from above.

In this embodiment, the first flow path portion 83 and the second flow path portion 84 constitute an oil path of the oil supply member 80 . Further, the oil recovery portion 82 connects the inner surface of the transmission case 2 (gear case 4) and the oil path. As a result, the oil recovered by the oil recovery portion 82 of the oil supply member 80 flows into the oil path, is guided by the oil path (the first flow path portion 83 and the second flow path portion 84), and flows into the first supply path. It is discharged from the portion 84a toward the drive gear 48 for reduction.

The oil path of this embodiment is a restricted flow path. In other words, as shown in FIG. 6, the width of the oil path of the oil supply member 80 (the dimension in the direction orthogonal to the direction of oil flow) is greater than that of the second flow path portion 84 on the upstream side of the first flow path portion 83 . is smaller on the downstream side. Specifically, the width W1 of the oil path in the first supply portion 84a of the oil supply member 80 is smaller than the width W2 of the oil path on the upstream side of the first flow path portion 83 of the oil supply member 80 . Further, the width W1 of the oil path in the first supply portion 84a of the oil supply member 80 is smaller than the dimension A of the reduction drive gear 48 in the axial direction (front-rear direction).

As shown in FIG. 5, the second supply section 85 is a plate-like member provided below the first supply section 84a and extending downward. The second supply portion 85 of the present embodiment is arranged on the left side of the first supply portion 84a in the left-right direction. Further, referring to FIG. 6, the second supply portion 85 is arranged so as to overlap with the reduction drive gear 48 in top view. Further, as shown in FIGS. 6 and 8, the second supply portion 85 is arranged radially outside the reduction drive gear 48 relative to the first supply portion 84a. The second supply portion 85 is arranged on the front side of the reduction drive gear 48 .

A dimension B of the second supply portion 85 in the front-rear direction is smaller than a dimension A of the reduction drive gear 48 in the axial direction (the front-rear direction). Further, the dimension B in the front-rear direction of the second supply portion 85 is larger than the width W1 of the oil path in the first supply portion 84a. The first supply portion 84a is arranged on the front side of the second supply portion 85 in the front-rear direction.

FIG. 9 is a cross-sectional perspective view for explaining the mounting structure of the oil supply member 80 to the gear case 4. As shown in FIG. Referring to FIG. 9, the bearing housing 60 is provided with two mounting holes 61 configured to allow the two front mounting portions 80a of the oil supply member 80 to be inserted respectively. Further, the bearing support wall 70 of the gear case 4 is provided with a mounting recess 74 configured so that the rear side mounting portion 80b of the oil supply member 80 can be inserted. The front mounting portion 80a of the oil supply member 80 is inserted into the mounting hole 61 of the bearing housing 60, and the rear mounting portion 80b is inserted into the mounting recess 74 of the bearing support wall 70. is placed between

The oil supply member 80 of the present embodiment is attached to the gear case 4 so that the first end surface 82a of the oil collecting portion 82 is arranged rearward in the front-rear direction relative to the rear end surface 70a of the bearing support wall 70. . Further, the oil supply member 80 of the present embodiment is attached to the gear case 4 so that the second end surface 82c of the oil recovery portion 82 of the present embodiment and the top surface 70d continuous with the side surface 70b are substantially flush with each other. It is

In the present embodiment, the distance between the first end surface 82a and the second end surface 82c of the oil recovery portion 82 is substantially the same as the dimension of the side surface 70b in the front-rear direction.

(oil flow)
The flow of oil inside the manual transmission 1 described above will be described.

First, as indicated by arrows F1 to F3 in FIGS. 1 and 2, the oil stored in the oil storage portion 7 is scraped upward by the rotation of the transmission gear 40 provided on the counter shaft 14 in the rotational direction R2. Raised. In particular, the oil that is raked up by the outer peripheral tooth portions of the first and second driven gears 41 and 42 is guided by the oil baffle 53 and efficiently raked upward.

Next, as indicated by arrows F4 and F5 in FIG. 2, the oil path 55 receives the scraped oil. As indicated by arrow F6 in FIGS. 1 and 2, the oil guided rearward through the first passage 56 positioned above in the oil path 55 is supplied to the lower input shaft 12 through a plurality of oil holes 56a. It is supplied to the upper input gear 30 . The oil supplied to the input gear 30 reaches the oil reservoir 7 while lubricating each part on the lower counter shaft 14 or directly.

Further, as indicated by an arrow F7 in FIG. 2, the oil guided rearward through the second passage 58 positioned below in the oil path 55 is supplied to the third space S3. A portion of the oil supplied to the third space S3 is stored in the third space S3 and is introduced into the output shaft 13 to lubricate each portion on the input shaft 12 or each portion on the output shaft 13 while supplying the oil. It reaches the reservoir 7 .

3 and 4, part of the oil stored in the third space S3 passes through the insertion hole 71 formed in the bearing support wall 70 of the gear case 4, It flows out into the second space S2. The oil that has flowed out into the second space S2 flows downward along the inner surface of the gear case 4 . This oil is guided to the oil collecting portion 82 of the oil supply member 80 by the guiding portion 72 .

At this time, even if the manual transmission 1 (or the vehicle on which the manual transmission 1 is mounted) is tilted forward, the oil that has flowed out into the second space S2 will move vertically as indicated by arrow F81 in FIG. It can drop and be collected in the oil collecting portion 82 of the oil supply member 80 . On the other hand, even if the manual transmission 1 (or the vehicle in which the manual transmission 1 is mounted) is tilted rearward, the oil that has flowed into the second space S2 is directed to the second space S2 as indicated by the arrow F8 in FIG. By flowing along the rear end face 70 a forming the portion 72 , the oil is recovered by the oil recovery portion 82 of the oil supply member 80 .

Further, even if the manual transmission 1 (or the vehicle on which the manual transmission 1 is mounted) leans to the right, the oil that has flowed out into the second space S2 will flow into the guide portion 72 as indicated by arrow F82 in FIG. is recovered by the oil recovery portion 82 of the oil supply member 80 by flowing along the side surface 70b forming the . Similarly, even if the manual transmission 1 (or the vehicle on which the manual transmission 1 is mounted) leans to the left, as indicated by arrow F82 in FIG. The oil is recovered by the oil recovery portion 82 of the oil supply member 80 by flowing along the side surface 70 c forming the oil supply member 80 .

As indicated by arrow F9 in FIGS. 5 and 6, the oil collected in the oil supply member 80 flows through the first flow path portion 83 and the second flow path portion 84, and flows from the first supply portion 84a to the deceleration drive. It is discharged toward gear 48 .

The oil discharged toward the reduction drive gear 48 lubricates the reduction drive gear 48 as indicated by an arrow F10 in FIG. Also, part of the oil discharged toward the reduction drive gear 48 is flipped off and scattered by the rotation of the reduction drive gear 48 .

As indicated by an arrow F11 in FIG. 8, part of the oil scattered by the rotation of the speed reduction drive gear 48 adheres to the downwardly extending portion 84b of the oil supply member 80, travels downward along the downwardly extending portion 84b, and flows downward. , and drips onto the reduction drive gear 48 from the lower end of the downwardly extending portion 84b.

8, part of the oil scattered by the rotation of the reduction drive gear 48 adheres to the second supply portion 85 of the oil supply member 80 and travels along the second supply portion 85. , and drips onto the reduction drive gear 48 from the lower end of the second supply portion 85 .

In addition, as shown in FIG. 6, in the present embodiment, the reduction drive gear 48 is a helical gear. It is configured to scatter to one side (rear side in the front-rear direction). Therefore, part of the oil discharged from the first supply portion 84a is scattered obliquely rearward toward the oil supply member 80 by the reduction drive gear 48, as indicated by an arrow F13 in FIG. This oil adheres to the second supply portion 85, flows along the second supply portion 85, and drips onto the reduction drive gear 48 from the lower end of the second supply portion 85 behind the first supply portion 84a. .

As a result, part of the oil that is discharged from the first supply portion 84a of the oil supply member 80, is scattered by the reduction drive gear 48 and does not contribute to lubrication of the reduction drive gear 48, is transferred to the downward extension portion 84b or the second oil supply portion 84b. It is again supplied from the No. 2 supply portion 85 to the reduction drive gear 48 .

According to the lubricating structure of the transmission according to the above embodiment, the following operational effects are obtained.

(1) The oil that runs along the inner surface of the transmission case 2 is recovered by the oil recovery portion 82 of the oil supply member 80 and supplied to the reduction drive gear 48 . In other words, the oil running along the inner surface of the transmission case 2 is used to lubricate the reduction drive gear 48 . As a result, the reduction drive gear 48 is efficiently lubricated with a small amount of oil, so that the oil level L in the transmission case 2 can be lowered. Further, when the oil level L in the transmission case 2 is lowered, the amount of oil stirred by the rotation of the speed change gear 40 including the reduction drive gear 48 is reduced, thereby reducing the stirring resistance and improving the fuel efficiency. can be achieved. As a result, by efficiently lubricating the reduction drive gear 48, it is possible to sufficiently lubricate the reduction drive gear 48 and reduce agitation resistance, thereby improving fuel efficiency.

(2) Since the bearing support wall 70 is formed with the guide portion 72 that guides the oil to the oil recovery portion 82 of the oil supply member 80 , the oil traveling along the inner surface of the bearing support wall 70 is efficiently removed by the oil recovery portion 82 . can be recovered.

(3) If the first end surface 82a of the oil recovery portion 82 is arranged forward in the front-rear direction of the rear end surface 70a of the bearing support wall 70, the oil flowing along the rear end surface 70a is It may not be possible to collect due to the first end surface 82a. In contrast, according to the present embodiment, the first end surface 82a of the oil collecting portion 82 is arranged rearward in the front-rear direction from the rear end surface 70a of the bearing support wall 70, so that the oil is transmitted through the rear end surface 70a. Oil can be recovered without fail. Further, even if the oil supply member 80 is displaced forward to such an extent that the first end surface 82a of the oil recovery portion 82 and the rear end surface 70a of the bearing support wall 70 are flush with each other, the oil recovery portion 82 does not have the rear end surface 70a. Can reliably collect the oil that travels through In other words, according to this configuration, it is possible to allow the positional deviation of the oil supply member 80 in the front-rear direction.

(4) Since the speed reduction drive gear 48 has a smaller diameter than the transmission gears 40 other than the speed reduction drive gear 48, when the oil level is lowered in order to improve fuel efficiency, the oil is stored in the oil reservoir 7. It is difficult to soak in the oil that has been applied. According to the transmission lubrication structure according to the present embodiment, the oil supply member 80 efficiently supplies oil to the reduction drive gear 48, so that the amount of oil supplied to the reduction drive gear 48 is ensured. In addition, the fuel efficiency can be improved.

Various changes and modifications may be made without departing from the spirit and scope of the invention as set forth in the claims.

For example, in the above embodiment, the oil supply member 80 is provided for lubricating the reduction drive gear 48, but is not limited to this, and is provided for lubricating other components that require lubrication. may be

1 Manual Transmission 2 Transmission Case 3 Clutch Housing 4 Gear Case 6 Magnet 7 Oil Reservoir 10 Gear Train 11 Main Shaft 12 Input Shaft 13 Output Shaft 14 Counter Shaft 21 to 26 First to Sixth Bearings 30 Input Gear 40 Transmission Gear 48 Reduction drive gear (Lubricated parts)
51 Oil separator 53 Oil baffle 55 Oil path 60 Bearing housing 70 Bearing support wall 70a Rear end surface (inner surface of transmission case)
70b, 70c side surface 71 insertion hole 72 guide portion 73 mounting hole 74 mounting recess 80 oil supply member 80a front side mounting portion 80b rear side mounting portion 81 body portion 82 oil recovery portion 82a first end surface 82b bottom surface 82c second end surface 83 first flow Path portion 84 Second flow path portion 84a First supply portion 84b Downward extension portion 85 Second supply portion

Claims (3)

a transmission case that accommodates a member to be lubricated;
an oil supply member having an oil path that guides oil to the member to be lubricated,
The oil supply member is provided with an oil recovery portion that connects the inner surface of the transmission case and the oil path,
The oil recovery unit is
a first end surface positioned outside the transmission case relative to the inner surface of the transmission case;
a second end surface facing the first end surface inside the transmission case relative to the first end surface;
A transmission lubrication structure. 2. The transmission lubrication structure according to claim 1, wherein said transmission case is formed with a guide portion for guiding oil to said oil recovery portion. 3. The transmission lubrication structure according to claim 1 , wherein said lubrication target member is a reduction gear of an output reduction type transmission.

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