JP6308061B2 - Transmission lubrication mechanism - Google Patents

Description

  The present invention relates to a transmission lubrication mechanism, and more particularly, to a transmission lubrication mechanism that partitions an oil reservoir chamber and a space where a countershaft is installed by an oil separator.

  2. Description of the Related Art Conventionally, a transmission lubrication mechanism mounted on a vehicle such as an automobile is provided with a rectifying plate as an oil separator below a transmission gear mechanism of the transmission. The rectifying plate is formed along the outer shape of the gear in the transmission gear mechanism, reduces the amount of oil that the gear contacts, reduces the agitation resistance by the oil, and improves the fuel consumption of the vehicle.

  As this type of conventional rectifying plate, the one described in Patent Document 1 is known. The rectifying plate is formed in a semicircular arc shape with an open top, and the rectifying plate is installed below the counter shaft and the counter gear. Thereby, the space in which the oil is stored and the space in which the counter shaft is installed are partitioned by the current plate.

JP 2012-102913 A

  However, since the conventional rectifying plate is formed in a semicircular arc shape with an open top, the rigidity is small, and heat changes due to heating and cooling when the rectifying plate is molded, and the heat of high-temperature oil Therefore, there is a possibility that both ends in the circumferential direction of the current plate are deformed in the opening direction.

  As a result, the regular gap between the rectifying plate and the counter gear cannot be kept uniform, and the amount of oil scraped up by the counter gear from the wide gap between the rectifying plate and the counter gear increases. For this reason, there exists a possibility that the stirring resistance of a counter gear may increase.

  In addition, since the gap between the rectifying plate and the counter gear is widened, the amount of oil dripped after being scraped up by the counter gear from the gap between the rectifying plate and the counter gear to the bottom surface of the rectifying plate It accumulates more than above. Thereby, there exists a possibility that the stirring resistance of a counter gear may increase more.

  The present invention has been made paying attention to the above-described problems, and an object of the present invention is to provide a lubrication mechanism for a transmission that can prevent an increase in agitation resistance of a counter gear.

A first aspect of the present invention includes an input shaft that has a plurality of input gears in the axial direction, rotates under the power from the internal combustion engine, and is disposed below the input shaft, and is selective to the input gear in the axial direction. A counter shaft having a plurality of counter gears meshing with each other, and having an oil separator mounted on a case body having an oil reservoir chamber in which oil is stored so that a part of the counter gear is immersed in the bottom portion. A lubrication mechanism for a transmission that extends along the axial direction of the countershaft so as to cover the gear and the countershaft, thereby partitioning the oil reservoir chamber and the space where the countershaft is installed by the oil separator. The cross-sectional shape perpendicular to the axial direction of the countershaft is an arc. And has a cylindrical portion surrounding the counter gear in the circumferential direction of the central axis of the counter shaft in an angular range of more than half a circle, and the oil separator is input to the lower outer peripheral surface of the counter gear and the counter shaft. shaft and has an outer peripheral surface of the counter gear on the opposite side covered cracks in the cylindrical portion, the case body and having an opening in the axial end portion, the partition wall is provided in the axial end portion, the cylindrical portion Is formed such that the longitudinal cross-sectional area gradually decreases from one axial end portion of the cylindrical portion toward the other axial end portion, and the counter gear having the largest diameter among the plurality of counter gears is connected to one axial end portion of the cylindrical portion. It consists of what is installed on the side .

  As described above, according to the first aspect, the oil separator is formed so that the cross-sectional shape orthogonal to the axial direction of the countershaft is an arc shape, and the counter gear is angled by a half or more in the circumferential direction of the central axis of the countershaft. It has a cylindrical part that surrounds the area.

  Thereby, the rigidity of an oil separator can be made high. For this reason, thermal deformation of the oil separator due to heating and cooling during molding of the oil separator can be suppressed, and thermal deformation of the oil separator due to high-temperature oil can be suppressed.

  For this reason, when the oil separator is assembled to the case body and then assembled to the counter shaft and the counter gear, the gap between the cylinder portion of the oil separator and the counter gear maintains a regular gap, and The surface can be brought close to the outer peripheral surface of the counter gear.

  Therefore, the amount of oil that enters between the inner peripheral surface of the cylinder portion and the outer peripheral surface of the counter gear can be reduced, the amount of oil scraped up by the counter gear can be reduced, and the stirring resistance of the counter gear can be reduced.

Furthermore, the oil separator covers the lower outer peripheral surface of the counter gear and the outer peripheral surface of the counter gear located on the opposite side of the input shaft with respect to the counter shaft with a cylindrical portion.
As a result, it is possible to prevent a large amount of oil that has been scraped up by the counter gear and then dropped from colliding with the upper surface of the case body from entering the oil separator through the gap between the counter gear and the oil separator. The stirring resistance of the separator can be reduced more effectively.

FIG. 1 is a diagram showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is a side view of the transmission. FIG. 2 is a diagram showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is a developed view of the inside of the transmission. FIG. 3 is a diagram showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is a cross-sectional view taken along the direction of arrows III-III in FIG. FIG. 4 is a view showing an embodiment of the lubrication mechanism of the transmission according to the present invention, and is a perspective view of the transmission as viewed from the front case side. FIG. 5 is a diagram showing an embodiment of the transmission lubrication mechanism of the present invention, and is a perspective view showing the structure of the transmission inside the front case. 6 is a diagram showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is a cross-sectional view taken along the line IV-IV in FIG. 3. FIG. 7 is a view showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is a perspective view of an oil separator. FIG. 8 is a diagram showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is a sectional view taken in the direction of the arrows in FIG. 6VIII-VIII showing an assembled state of an oil separator and a rear case. FIG. 9 is a view showing an embodiment of a lubrication mechanism for a transmission according to the present invention, and is an exploded perspective view of a rear case, an oil separator, and a countershaft.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a lubrication mechanism for a transmission according to the present invention will be described with reference to the drawings.
FIGS. 1-9 is a figure which shows the lubrication mechanism of the transmission of one Embodiment which concerns on this invention.
First, the configuration will be described.
In FIG. 1, a transmission 30 is mounted on a vehicle 30 such as an automobile. The transmission 1 includes a front case 2 attached to an engine 10 as an internal combustion engine, and a rear case 3 attached to the front case 2. And an extension case 4 attached to the rear case 3.

  2 and 3, an input shaft 5 is rotatably supported by the front case 2, and the input shaft 5 rotates by receiving power from the engine 10. An output shaft 6 is rotatably supported on the rear case 3 and the extension case 4, and an input shaft 5 is supported at the tip of the output shaft 6 so as to be rotatable relative to the output shaft 6. Thereby, both front and rear direction ends of the input shaft 5 are supported by the front case 2 and the output shaft 6.

  The output shaft 6 is connected to a differential device (not shown), and the power of the output shaft 6 is transmitted to left and right drive wheels (not shown) via the differential device.

  In FIG. 2, a reverse idler shaft 7 is rotatably connected to the front case 2 and the rear case 3. A counter shaft 8 is rotatably supported by the front case 2 and the extension case 4, and the counter shaft 8 is positioned below the input shaft 5 (see FIGS. 4 and 5). It extends parallel to the shaft 7.

  2 and 3, the input shaft 5 is provided with a first speed input gear 11A, a reverse input gear 11B, a second speed input gear 11C, a fourth speed input gear 11D and a third speed input gear 11E in order from the front case 2 side. It has been.

  The first speed input gear 11 </ b> A, the reverse input gear 11 </ b> B, and the second speed input gear 11 </ b> D are fixed to the input shaft 5. The 4-speed input gear 11D and the 3-speed input gear 11E are rotatably provided on the input shaft 5.

  A 5-speed input gear 11 </ b> F is provided at one end of the output shaft 6, and the 5-speed input gear 11 </ b> F is constituted by a dog formed on the outer peripheral portion of the output shaft 6. Further, a reduction output gear 9 is provided on the outer periphery of one end portion of the output shaft 6, and the reduction output gear 9 rotates integrally with the output shaft 6.

  In FIG. 2, the counter shaft 8 includes a first speed counter gear 12A, a reverse output gear 12B, a second speed counter gear 12C, a fourth speed counter gear 12D, a third speed counter gear 12E, and a reduction input gear 12F in order from the front case 2 side. Is provided.

  The first speed counter gear 12A, the reverse output gear 12B and the second speed counter gear 12C are rotatably provided on the counter shaft 8. Further, the 4-speed counter gear 12D, the 3-speed counter gear 12E, and the reduction input gear 12F are fixed to the counter shaft 8.

  The reduction input gear 12F is meshed with the reduction output gear 9, and the reduction output gear 9 is attached to the output shaft 6 so as to rotate integrally with the output shaft 6.

  A reverse idler gear 13 is provided on the reverse idler shaft 7. The reverse idler gear 13 is rotatable integrally with the reverse idler shaft 7 and is movable in the axial direction of the reverse idler shaft 7, and meshes with the reverse input gear 11 </ b> B and the reverse output gear 12 </ b> B when the vehicle 30 moves backward. .

  Here, the 1st speed input gear 11A, the reverse input gear 11B, the 2nd speed input gear 11C, the 4th speed input gear 11D, and the 3rd speed input gear 11E constitute the input gear of the present invention. The first speed counter gear 12A, the reverse output gear 12B, the second speed counter gear 12C, the fourth speed counter gear 12D, and the third speed counter gear 12E constitute the counter gear of the present invention.

  The transmission 1 of the present embodiment includes a first speed input gear 11A, a reverse input gear 11B, a second speed input gear 11D, a fourth speed input gear 11D and a third speed input gear 11E, a fifth speed input gear 11F, and a first speed counter gear 12A. The reverse output gear 12B, the second speed counter gear 12C, the fourth speed counter gear 12D, the third speed counter gear 12E, and the reverse idler gear 13 are selectively meshed with each other, so that the first forward speed to the fifth speed and the first reverse speed can be achieved. The gear position is established.

  As a result, the rotation of the input shaft 5 is shifted and transmitted to the countershaft 8, the power is transmitted from the reduction input gear 12F of the countershaft 8 to the reduction output gear 9 of the output shaft 6, and the output shaft 6 rotates.

  1 to 3, a front case 2, a rear case 3, and an extension case 4 constitute a transmission case 14, and the rear case 3 constitutes a case body of the present invention.

  The rear case 3 has an opening 3A at one end in the axial direction, and a partition wall 3B is provided at the other end in the axial direction. The interior of the rear case 3 and the extension case 4 are partitioned by the partition 3B.

  2 and 6, the rear case 3 has an oil reservoir chamber 15 in which oil O is stored at the bottom of the rear case 3, and includes a first speed counter gear 12A, a reverse output gear 12B, a second speed counter gear 12C, and a fourth speed counter. The gear 12D, the third speed counter gear 12E, and the reduction input gear 12F are immersed in the oil O.

  An oil separator 16 is provided inside the rear case 3. In FIG. 5, the oil separator 16 extends along the axial direction of the counter shaft 8 so as to cover the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D, and the third speed counter gear 12E. The oil separator 16 partitions the oil reservoir chamber 15 from the space where the counter shaft 8 is installed.

  7 to 9, the oil separator 16 has a cylindrical portion 17. The cylindrical portion 17 is formed in a circular arc shape in cross section perpendicular to the axial direction of the countershaft 8, and the cylindrical portion 17 rotates the counter gear halfway around the central axis C of the countershaft 8 (see FIG. 6). It is surrounded by the above angle range.

  The cylindrical portion 17 of the present embodiment has a first-speed counter gear 12A, a second-speed counter gear 12C, a fourth-speed counter gear 12D, and a third-speed counter gear 12E in the circumferential direction of the central axis C of the countershaft 8 as an angular range of half or more. Is surrounded by an angle range of 3/4 or more.

  Further, the cylindrical portion 17 has a lower outer peripheral surface of the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D and the third speed counter gear 12E, and the counter shaft 8 in an angle range of 3/4 round or more. The first-speed counter gear 12A, the second-speed counter gear 12C, the fourth-speed counter gear 12D, and the third-speed counter gear 12E that are located on the opposite side of the input shaft 5 are covered.

  Specifically, in FIG. 6, the countershaft 8 is installed obliquely below the input shaft 5, and the cylinder portion 17 includes a second speed counter gear 12 </ b> C and a first speed input gear when viewed in the axial direction of the oil separator 16. 11C has a circumferential one end 17a located below the meshing portion B with 11C, and a circumferential other end 17b extending from the circumferential one end 17a below the counter shaft 8 and above the second speed counter gear 12C. . The axial direction of the oil separator 16 is the same as the axial direction of the input shaft 5.

  In FIG. 6, the meshing portion B between the second-speed counter gear 12C and the first-speed input gear 11C is described, but the first-speed input gear 11A, the fourth-speed input gear 11D, the third-speed input gear 11E, and the first-speed counter Needless to say, the gears 12A, 4th counter gear 12D and 3rd speed counter gear 12E extend from below the respective meshing portions to below the counter shaft 8 and above the 2nd speed counter gear 12C.

  7-9, the cylinder part 17 is formed so that a longitudinal cross-sectional area may become small gradually toward the axial direction other end part 17d from the axial direction one end part 17c of the cylindrical part 17, The axial direction of the cylindrical part 17 The one end portion 17c constitutes the large diameter portion 17A, and the other axial end portion 17d of the cylindrical portion 17 constitutes the small diameter portion 17B.

2 and 9, among the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D and the third speed counter gear 12E, the first speed counter gear 12A installed on the front case 2 side has the maximum diameter. The counter gear is configured.
4, 5, and 9, the maximum-diameter first-speed counter gear 12 </ b> A is installed in the large-diameter portion 17 </ b> A of the cylindrical portion 17 on the axial direction one end portion 17 c side.

  7-9, the cylinder part 17 has several level | step-difference parts 17D and 17E to which a longitudinal cross-sectional area reduces toward the axial direction other end part 17d from the axial direction one end part 17c. Thereby, the cylinder part 17 continues to the large diameter part 17A having the tapered outer periphery via the stepped parts 17D and 17E, the small diameter part 17B, the large diameter part 17A and the small diameter part 17B, and the large diameter part. It has a medium diameter portion 17C having a smaller diameter than 17A and a larger diameter than the small diameter portion 17B.

  In FIG. 7, a strip-shaped connecting portion 18 is provided at the other axial end 17 d of the cylindrical portion 17, and the connecting portion 18 is connected to the circumferential one end 17 a that is both ends in the circumferential direction of the cylindrical portion 17 and the circumferential direction. The other end 17b is connected.

  7 and 8, fitting pins 19 a and 19 b are formed on the outer peripheral portion of the large diameter portion 17 </ b> A, and the fitting pins 19 a and 19 b extend in the axial direction of the cylindrical portion 17. In FIG. 8, fitting holes 3 a and 3 b are formed in the inner peripheral portion of the rear case 3, and the fitting holes 3 a and 3 b are formed on the opening 3 A side of the rear case 3.

  The fitting holes 3a and 3b extend in the same direction as the axial direction of the cylindrical portion 17, and fitting pins 19a and 19b are fitted into the fitting holes 3a and 3b. Here, fitting pin 19a, 19b comprises the 1st fitting part of this invention, and fitting hole 3a, 3b comprises the 1st fitting hole of this invention.

  7 and 8, a fitting pin 19c is formed on the outer peripheral portion of the small diameter portion 17B, and the fitting pin 19c extends in the axial direction of the cylindrical portion 17. In FIG. 8, a fitting hole 3 c is formed in the inner peripheral portion of the rear case 3, and the fitting hole 3 c is formed on the partition wall 3 </ b> B side of the rear case 3.

  The fitting hole 3c extends in the same direction as the axial direction of the cylindrical portion 17, and the fitting pin 19c is fitted into the fitting hole 3c. Here, the fitting pin 19c constitutes the second fitting portion of the present invention, and the fitting hole 3c constitutes the second fitting hole of the present invention.

In addition, the axial length L1 of the fitting pins 19a and 19b is longer than the axial length L2 of the fitting pin 19c, and the axial lengths of the fitting pins 19a and 19b are approximately the same. It is formed in length.
7 and 8, a bulging portion 20 is formed on the outer peripheral portion of the large diameter portion 17A, and the bulging portion 20 bulges outward in the radial direction of the large diameter portion 17A.

  The fitting pin 19b is formed on the side wall 20a of the bulging portion 20 facing the small diameter portion 17B, and the fitting pin 19a and the fitting pin 19b are displaced in the axial direction of the cylindrical portion 17.

  The fitting pin 19c is formed in the outer peripheral part of the cylinder part 17 in which the bulging part 20 is provided in the circumferential direction of the small diameter part 17B, and the fitting pin 19b and the fitting pin 19c formed in the bulging part 20 are formed. Is installed in an overlapping manner in the axial direction of the cylindrical portion 17.

  In FIG. 8, a plurality of oil holes 17 e are formed in the cylinder portion 17, and the oil holes 17 e are immersed in the oil O. Thereby, oil is stored in the inner peripheral part of the cylinder part 17 through the oil hole 17e.

Next, the operation will be described.
In FIG. 6, when the input shaft 5 rotates in the clockwise direction R1 when the vehicle 30 moves forward, the counter shaft 8 rotates in the counterclockwise direction R2. As the counter shaft 8 rotates in the counterclockwise rotation direction R2, the oil O is scraped up by the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D, and the third speed counter gear 12E.
Accordingly, the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D and the third speed counter gear 12E, the first speed input gear 11A, the second speed input gear 11C, the fourth speed input gear 11D, and the third speed input gear 11E. Is engaged with oil O1.

  The oil separator 16 partitions the oil reservoir chamber 15 from the space where the counter shaft 8 is installed, so that the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D, and the third speed counter gear 12E are oil reservoirs. It is possible to prevent immersion in the entire oil O in the chamber 15.

  Thereby, the agitation resistance due to the oil O of the first speed counter gear 12A, the second speed counter gear 12C, the fourth speed counter gear 12D and the third speed counter gear 12E can be reduced, and the fuel consumption of the engine 10 can be improved.

  According to the lubrication mechanism of the transmission 1 of the present embodiment, the oil separator 16 has a cross-sectional shape orthogonal to the axial direction of the countershaft 8 formed in an arc shape, and a 1-speed counter in the circumferential direction of the central axis of the countershaft 8. It has a cylindrical portion 17 that surrounds the gear 12A and the like within an angular range of half a circumference or more.

  Thereby, the rigidity of the oil separator 16 can be increased. For this reason, thermal deformation of the oil separator 16 due to heating and cooling during molding of the oil separator 16 can be suppressed, and thermal deformation of the oil separator 16 due to high-temperature oil can be suppressed.

  For this reason, when the oil separator 16 is assembled to the rear case 3 and then assembled to the counter shaft 8 and the first speed counter gear 12A, etc., the cylinder portion 17 of the oil separator 16 and the first speed counter gear 12A, etc. A regular gap is maintained, and the inner peripheral surface of the cylindrical portion 17 and the outer peripheral surface of the first-speed counter gear 12A and the like can be brought close to each other.

  Therefore, it is possible to reduce the amount of oil scooped up by the first speed counter gear 12A or the like by reducing the amount of oil entering between the inner peripheral surface of the cylindrical portion 17 and the outer peripheral surface of the first speed counter gear 12A or the like. Agitation resistance of the gear 12A and the like can be reduced.

  Further, the oil separator 16 has a cylindrical portion 17 that connects a lower outer peripheral surface of the first speed counter gear 12A and the like and an outer peripheral surface of the first speed counter gear 12A and the like positioned on the opposite side of the input shaft 5 with respect to the counter shaft 8. Covering.

  As a result, oil that has been scraped up by the first-speed counter gear 12A or the like and then collides and drops on the upper surface of the rear case 3 enters the oil separator 16 from the gap between the first-speed counter gear 12A or the like and the oil separator 16. It is possible to prevent a large amount from entering, and to more effectively reduce the stirring resistance of the oil separator 16.

  Further, since the rigidity of the oil separator 16 can be increased, it is possible to suppress deformation of the oil separator 16 due to a load applied to the oil separator 16 when the oil separator 16 is assembled to the rear case 3. The burden of the assembly work of the oil separator 16 can be reduced, and the workability of the assembly workability of the oil separator 16 can be improved.

  Further, according to the oil separator 16 of the present embodiment, the cylindrical portion 17 is formed such that the longitudinal sectional area gradually decreases from the axial one end portion 17c toward the axial other end portion 17d, and a plurality of 1-speed counter gears 12A, the 2nd speed counter gear 12C, the 4th speed counter gear 12D, and the 3rd speed counter gear 12E, the 1st speed counter gear 12A of the maximum diameter is installed in the axial direction one end part 17c of the cylinder part 17. As shown in FIG.

  Thereby, it can be made the shape which improves the rigidity of the cylinder part 17. FIG. For this reason, thermal deformation of the oil separator 16 due to heating and cooling during molding of the oil separator 16 can be more effectively suppressed, and thermal deformation of the oil separator 16 due to high-temperature oil can be more effectively suppressed.

  Further, the oil separator 16 can be easily assembled to the rear case 3 by assembling the cylindrical portion 17 to the rear case 3 from the other axial end 17d of the cylindrical portion 17 having the small diameter portion 17B.

  Thereafter, the countershaft 8 having the first-speed counter gear 12A and the like attached to the oil separator 16 is assembled by assembling the countershaft 8 to the oil separator 16 from the axial direction one end 17c side of the cylindrical portion 17 constituting the large diameter portion 17A. Can be assembled easily.

  Moreover, since the assembly direction of the oil separator 16 and the counter shaft 8 can be made the same direction, the workability of the assembly work of the oil separator 16, the counter shaft 8, the first speed counter gear 12A, etc. can be improved more effectively.

  Further, according to the oil separator 16 of the present embodiment, the cylindrical portion 17 includes the plurality of stepped portions 17D and 17E whose longitudinal cross-sectional area decreases from the axial one end 17c to the axial other end 17d of the cylindrical portion 17. Have.

  Thereby, the rigidity of the oil separator 16 can be improved more effectively, the thermal deformation of the oil separator 16 due to heating and cooling during the molding of the oil separator 16 can be more effectively suppressed, and the oil separator 16 of high-temperature oil can be prevented. Thermal deformation can be more effectively suppressed.

  In addition, it is possible to more effectively suppress deformation of the oil separator 16 due to a load applied to the oil separator 16 when the oil separator 16 is assembled to the rear case 3. For this reason, the workability of the assembly workability of the oil separator 16 can be improved more effectively.

  In addition, according to the oil separator 16 of the present embodiment, the connecting portion 18 that connects the circumferential one end 17a and the circumferential other end 17b of the cylindrical portion 17 is provided to the other axial end 17d of the cylindrical portion 17. .

  Thereby, thermal deformation of the oil separator 16 due to heating and cooling during molding of the oil separator 16 can be more effectively suppressed, and thermal deformation of the oil separator 16 due to high-temperature oil can be more effectively suppressed.

  Therefore, the oil separator 16 can be more effectively prevented from opening in the circumferential direction, and a regular gap can be maintained between the cylinder portion 17 of the oil separator 16 and the first-speed counter gear 12A and the like.

  Further, according to the oil separator 16 of the present embodiment, the connecting portion 18 is provided at the other axial end 17d of the cylindrical portion 17 having a smaller diameter than the other axial end 17d of the cylindrical portion 17. The overall length can be shortened, and the oil separator 16 can be more effectively prevented from opening in the circumferential direction.

  Further, according to the lubrication mechanism of the transmission 1 according to the present embodiment, when the oil separator 16 is viewed in the axial direction, the cylindrical portion 17 is countered from below the meshing portion between the first-speed counter gear 12A and the first-speed input gear 11C. The first speed counter gear 12 </ b> A and the like extend above the shaft 8.

  As a result, the oil O1 (see FIG. 6) that collides and drops on the upper surface of the rear case 3 after being scooped up by the first-speed counter gear 12A or the like is moved in the circumferential direction of the cylindrical portion 17 that extends above the first-speed counter gear 12A or the like. It can be blocked on the other end 17b side. For this reason, it is possible to prevent a large amount of oil from entering the inside of the oil separator 16, and to reduce the stirring resistance of the oil separator 16 more effectively.

Further, according to the oil separator 16 of the present embodiment, the cylindrical portion 17 surrounds the first speed counter gear 12A and the like in the circumferential direction of the central axis of the countershaft 8 in an angle range of 3/4 or more.
Thereby, the rigidity of the oil separator 16 can be further increased. For this reason, thermal deformation of the oil separator 16 due to heating and cooling during molding of the oil separator 16 can be more effectively suppressed, and thermal deformation of the oil separator 16 due to high-temperature oil can be more effectively suppressed.

  Therefore, when the counter shaft 8 and the first-speed counter gear 12A are assembled to the oil separator 16 after the oil separator 16 is assembled to the rear case 3, the gap between the cylindrical portion 17 of the oil separator 16 and the first-speed counter gear 12A or the like. Can be kept close to the inner peripheral surface of the cylindrical portion 17 and the outer peripheral surface of the first speed counter gear 12A or the like.

  As a result, the amount of oil entering between the inner peripheral surface of the cylindrical portion 17 and the outer peripheral surface of the first speed counter gear 12A and the like can be reduced, and the amount of oil scraped up by the first speed counter gear 12A and the like can be reduced. Agitation resistance of the counter gear 12A and the like can be reduced.

  Further, the other end 17b in the circumferential direction of the cylindrical portion 17 can be reliably extended above the first-speed counter gear 12A and the like, so that it collides with the upper surface of the rear case 3 after being scraped up by the first-speed counter gear 12A and the like. The oil O1 dripping in this manner can be reliably blocked at the other end portion 17b in the circumferential direction of the cylindrical portion 17 extending upward such as the first-speed counter gear 12A.

  Therefore, it is possible to prevent a large amount from entering the inside of the oil separator 16, and the stirring resistance of the oil separator 16 can be more effectively reduced.

  Further, according to the lubrication mechanism of the transmission 1 of the present embodiment, the large-diameter portion 17A is fitted in the fitting holes 3a and 3b extending in the axial direction of the cylindrical portion 17 and formed in the rear case 3 on the opening 3A side. Fitting pins 19a and 19b to be joined are formed, the small-diameter portion 17B extends in the axial direction of the cylindrical portion 17, and the fitting pin 19c is fitted into a fitting hole 3c formed on the partition wall 3B side of the rear case 3. Is formed.

  Thus, when the oil separator 16 is assembled to the rear case 3, the large diameter portion 17A can be attached to the rear case 3 via the fitting pins 19a and 19b, and the small diameter portion 17B can be attached to the rear case 3 via the fitting pin 19c. Can be assembled.

Here, it is sufficient that at least one fitting pin is formed on the large diameter portion 17A, and at least one fitting pin is formed on the small diameter portion 17B.
Further, according to the oil separator 16 of the present embodiment, the axial length L1 of the fitting pins 19a and 19b is formed longer than the axial length L2 of the fitting pin 19c.

Accordingly, when the fitting pins 19a and 19b of the large diameter portion 17A are fitted into the fitting holes 3a and 3b located on the opening 3A side of the rear case 3, the large diameter portion is located on the back side of the rear case 3. With 17A, the fitting pin 19c of the small-diameter portion 17B that is difficult for the operator to visually check can be positioned in the fitting hole 3c, and the fitting pin 19c can be fitted into the fitting hole 3c.
For this reason, the oil separator 16 can be easily assembled to the rear case 3, and the workability of the assembly work of the oil separator 16 can be improved.

  Further, according to the lubrication mechanism of the transmission 1 of the present embodiment, the bulging portion 20 bulging outward in the radial direction of the large diameter portion 17A is formed on the outer peripheral portion of the large diameter portion 17A, and on the small diameter portion 17B side. The fitting pin 19b was formed in the side wall 20a of the bulging part 20 which faces. In addition, in the circumferential direction of the small diameter portion 17B, a fitting pin 19c is formed on the outer peripheral portion of the small diameter portion 17B where the bulging portion 20 is provided, and the fitting pin 19b formed on the bulging portion 20 is fitted. The pin 19c was placed so as to overlap in the axial direction of the cylindrical portion 17.

  Accordingly, as shown in FIG. 9, when the oil separator 16 is inserted into the rear case 3 from the opening 3A of the rear case 3 and the fitting pin 19c of the small diameter portion 17B is fitted into the fitting hole 3c, the fitting pin A larger pressing load is applied to the fitting pin 19b that overlaps the fitting pin 19c and the cylindrical portion 17 in the axial direction than 19a.

  However, the oil separator 16 of the present embodiment can increase the rigidity around the fitting pin 19b formed in the bulging portion 20 by the bulging portion 20, and the fitting pin 19b formed in the bulging portion 20 is deformed. Can be prevented. Therefore, the workability of the assembly work of the oil separator 16 when the oil separator 16 is assembled to the rear case 3 can be improved.

  While embodiments of the invention have been disclosed, it will be apparent to those skilled in the art that changes may be made without departing from the scope of the invention. All such modifications and equivalents are intended to be included in the following claims.

1. Transmission, 3 ... Rear case (case body), 3A ... Opening (case body opening), 3B ... Bulkhead (case bulkhead), 3a, 3b ... Joint hole (first fitting hole), 3c ... fitting hole (second fitting hole), 5 ... input shaft, 8 ... counter shaft, 10 ... engine (internal combustion engine) 11A ... 1st speed input gear (input gear), 11B ... Reverse input gear (input gear), 11C ... 2nd speed input gear (input gear), 11D ... 4th speed input gear (input gear) ), 11E ... 3rd speed input gear (input gear), 12A ... 1st speed counter gear, 12B ... Reverse output gear (counter gear), 12C ... 2nd speed counter gear (counter gear), 12D ... 4-speed counter gear (counter gear), 12E ... 3-speed counter gear (counter gear), 15 ... oil reservoir , 16 ... Oil separator, 17 ... Cylinder part, 17A ... Large diameter part, 17B ... Small diameter part, 17D, 17E ... Step part, 17a ... One circumferential end part (Cylinder part) One end in the circumferential direction), 17b ... the other end in the circumferential direction (the other end in the circumferential direction of the cylindrical portion), 17c ... one end in the axial direction (one end in the axial direction of the cylindrical portion), 17d ... the axis. Direction other end part (circumferential other end part of the cylinder part), 18 ... connection part, 19a, 19b ... fitting pin (first fitting part), 19c ... fitting pin (second Fitting part), 20 ... bulging part, 20a ... side wall (side wall of bulging part), B ... meshing part (meshing part of counter gear and input gear), C ... counter shaft Center axis

Claims (8)

An input shaft having a plurality of input gears in the axial direction and rotating by receiving power from the internal combustion engine, and a plurality of counter gears installed below the input shaft and selectively meshing with the input gears in the axial direction. An oil separator mounted on a case body having an oil reservoir chamber in which oil that stores a part of the counter gear is stored at the bottom.
The oil separator extends along the axial direction of the countershaft so as to cover the countergear and the countershaft, so that the oil separator partitions the oil reservoir chamber from the space where the countershaft is installed. A lubrication mechanism for a transmission,
The oil separator has a cylindrical portion whose cross-sectional shape orthogonal to the axial direction of the countershaft is formed in an arc shape, and which surrounds the counter gear in the circumferential direction of the central axis of the countershaft in an angular range of a half or more. ,
The oil separator, the lower outer peripheral surface of the counter gear, an outer peripheral surface of the counter gear on the opposite side to the input shaft to the counter shaft and cracks covered by the tubular portion,
The case body has an opening at one end in the axial direction, and a partition is provided at the other end in the axial direction.
The cylindrical portion is formed such that the longitudinal sectional area gradually decreases from one axial end of the cylindrical portion toward the other axial end,
A lubricating mechanism for a transmission , wherein a counter gear having a maximum diameter among the plurality of counter gears is installed on one end side in the axial direction of the cylindrical portion . 2. The transmission lubrication mechanism according to claim 1 , wherein the cylindrical portion has a plurality of stepped portions whose longitudinal cross-sectional area decreases from one axial end portion of the cylindrical portion toward the other axial end portion . The transmission according to claim 1 or 2 , wherein a connecting portion that connects one end portion in the circumferential direction and the other end portion in the circumferential direction of the cylindrical portion is provided at the other axial end portion of the cylindrical portion. Lubrication mechanism. The counter shaft is installed obliquely below the input shaft;
2. The axial direction of the oil separator, the cylindrical portion extends from below a meshing portion of the counter gear and the input gear to above the counter gear through a lower portion of the counter shaft. A lubrication mechanism for a transmission according to any one of claims 3 to 4. The said cylinder part surrounds the said counter gear in the circumferential direction of the center axis | shaft of the said counter shaft in the angle range more than 3/4 round, The Claim 1 characterized by the above-mentioned. Transmission lubrication mechanism. One end in the axial direction of the cylindrical portion constitutes a large diameter portion, and the other axial end of the cylindrical portion constitutes a small diameter portion,
At least one first fitting portion that extends in the axial direction of the cylindrical portion and is fitted in a first fitting hole formed on the opening side of the case body is formed in the large diameter portion. Formed,
At least one second fitting portion that extends in the axial direction of the cylindrical portion and fits into a second fitting hole formed on the partition side of the case body is formed in the small diameter portion. lubrication mechanism for a transmission according to any one of claims 2 to 5, characterized in Rukoto. 7. The transmission lubrication mechanism according to claim 6 , wherein an axial length of the first fitting portion is longer than an axial length of the second fitting portion . On the outer periphery of the large diameter portion, a bulging portion that bulges outward in the radial direction of the large diameter portion is formed,
Forming one of the first fitting portions on the side wall of the bulging portion facing the small diameter portion;
In the circumferential direction of the small diameter portion, the second fitting portion is formed on the outer peripheral portion of the small diameter portion where the bulging portion is provided,
The said 1st fitting part and said 2nd fitting part which are formed in the said bulging part were piled up and installed in the axial direction of the said cylinder part, The Claim 6 or Claim 7 characterized by the above-mentioned. Transmission lubrication mechanism.

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