JP2019190474A - Rotary shaft support structure - Google Patents

Abstract

To provide a rotary shaft support structure which enables easy improvement of support rigidity of a bearing support part supporting a rotary shaft of a rotary member.SOLUTION: An automatic transmission 2 has a torque converter housing 5 which houses a torque converter having a turbine shaft and in which the turbine shaft is rotatably supported by a bearing support part 31a formed at a partition wall 31. The partition wall 31 has: an annular rib 31C which encloses the bearing support part 31a at the radial outer side of the bearing support part 31a; and an oil passage expansion part 32 to an oil passage expansion part 36 which extend downward from the annular rib 31C so as to expand from the partition wall 31 to the outer side in an axial direction of the turbine shaft 11 and respectively have an oil passage 32a to an oil passage 36a formed therein.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a support structure for a rotating shaft.

  Conventionally, as a transmission having a torque converter, there is one mounted on an industrial vehicle described in Patent Document 1. In a transmission mounted on an industrial vehicle, an input shaft connected to a turbine of a torque converter is rotatably supported on a bearing support portion of a torque converter housing via a bearing.

  An oil pump is provided on the input shaft, and hydraulic oil sucked by the oil pump is supplied to the torque converter through a torque converter hydraulic oil passage formed in the torque converter housing.

Japanese Patent No. 6168021

  In such a conventional transmission, a torque converter operating oil passage is formed in the torque converter housing, but the torque converter operating oil passage is a space that flows through the oil passage. Therefore, the rigidity of the torque converter housing is reduced by the amount of space formed in the torque converter housing, and the rigidity of the bearing support portion that supports the input shaft may be reduced.

  The present invention has been made paying attention to the above-described circumstances, and an object thereof is to provide a support structure for a rotating shaft that can easily improve the support rigidity of a bearing support portion that supports the rotating shaft of a rotating member. To do.

  The present invention is a rotating shaft support structure including a rotating member having a rotating shaft, and having a case that rotatably supports the rotating shaft on a bearing support portion formed on the wall portion. An annular reinforcing portion that surrounds the bearing supporting portion radially outward of the bearing supporting portion, and extends downward from the reinforcing portion so as to bulge outward from the wall portion in the axial direction of the rotating shaft, And a plurality of oil passage bulges each having an oil passage formed therein.

  As described above, according to the present invention, the support rigidity of the bearing support portion that supports the rotation shaft of the rotation member can be easily improved.

FIG. 1 is a left side view of an automatic transmission having a rotating shaft support structure according to an embodiment of the present invention. FIG. 2 is a longitudinal sectional view of an automatic transmission having a rotating shaft support structure according to an embodiment of the present invention, which is cut in a longitudinal direction along an input shaft. FIG. 3 is a rear view of a torque converter housing of an automatic transmission having a rotating shaft support structure according to an embodiment of the present invention. FIG. 4 is a left side view of a torque converter housing of an automatic transmission having a rotating shaft support structure according to an embodiment of the present invention. FIG. 5 is a right side view of a torque converter housing of an automatic transmission having a rotating shaft support structure according to an embodiment of the present invention. FIG. 6 is a bottom view of a torque converter housing of an automatic transmission having a rotating shaft support structure according to an embodiment of the present invention.

A rotary shaft support structure according to an embodiment of the present invention is a rotary shaft including a case that accommodates a rotary member having a rotary shaft and rotatably supports the rotary shaft on a bearing support portion formed on a wall portion. The wall portion includes an annular reinforcing portion that surrounds the bearing support portion in a radially outward direction of the bearing support portion, and a reinforcing portion that bulges outward from the wall portion in the axial direction of the rotating shaft. And a plurality of oil passage bulges having oil passages formed therein.
Thereby, the support rigidity of the bearing support part which supports the rotating shaft of a rotating member can be improved easily.

Hereinafter, a support structure for a rotating shaft according to an embodiment of the present invention will be described with reference to the drawings.
1 to 6 are views showing a support structure of a rotating shaft according to an embodiment of the present invention. In FIG. 1 to FIG. 6, in the up / down / front / rear / left / right directions, the vehicle width direction is the left / right direction and the vehicle height direction is the up / down direction when the vehicle traveling direction is the front and the backward direction is the rear.

First, the configuration will be described.
1 and 2, an automatic transmission 2 is mounted on a vehicle 1, and the automatic transmission 2 is installed vertically below a floor panel 1 </ b> A of the vehicle 1 while being connected to an engine 3. Yes. That is, the vehicle 1 of the present embodiment is a rear wheel drive vehicle.

  The automatic transmission 2 includes a transmission case 4, and the transmission case 4 includes a torque converter housing (hereinafter simply referred to as a torque converter housing) 5, a front case 6, a rear case 7, and an extension case 8. Yes.

  The torque converter housing 5 of the present embodiment constitutes a case of the present invention, and the front case 6 constitutes another case of the present invention. That is, the transmission case 4 includes a torque converter housing 5.

  An engine 3 as an internal combustion engine is connected to a front end portion of the torque converter housing 5 by a bolt (not shown). The engine 3 burns fuel and converts thermal energy into mechanical energy.

In FIG. 1, an annular joint 5 </ b> A is formed at the rear end of the torque converter housing 5.
A plurality of fastening portions 5B are formed at a predetermined interval in the circumferential direction in the joint portion 5A.

  In FIG. 2, the torque converter housing 5 side of the front case 6 is open. As shown in FIG. 1, an annular joint 6A is formed at the front end portion of the front case 6, and a plurality of fastening portions 6B are formed at predetermined intervals in the circumferential direction on the joint 6A. Yes. The fastening portion 6B is provided on the front case 6 so as to match the fastening portion 5B.

  Bolts (not shown) are attached to the fastening part 5B and the fastening part 6B, and the fastening part 5B and the fastening part 6B are fastened by bolts. Thereby, the torque converter housing 5 and the front case 6 are connected to each other in a state where the joint portion 5A and the joint portion 6A are joined. The fastening portion 5B of the torque converter housing 5 of the present embodiment constitutes a first fastening portion of the present invention, and the fastening portion 6B of the front case 6 constitutes a second fastening portion of the present invention.

  In FIG. 2, a torque converter 10 is accommodated in the torque converter housing 5. The torque converter 10 includes a front cover 10A connected to a crankshaft (not shown) of the engine 3 via a drive plate (not shown), and a shell 10B connected to the front cover 10A. And a fluid coupling that transmits power via oil.

  A pump impeller (not shown) is fixed to the inner surface of the shell 10B. Inside the shell 10 </ b> B, a turbine runner (not shown) is installed facing the pump impeller, and the turbine runner is connected to the turbine shaft 11. A stator (not shown) is installed between the pump impeller and the turbine runner.

  In the torque converter 10, when the crankshaft rotates, the front cover 10A, the shell 10B, and the pump impeller rotate integrally through the drive plate. At this time, due to the centrifugal force generated by the rotation of the pump impeller, a flow from the pump impeller to the turbine runner is generated in the fluid inside the torque converter 10, that is, oil.

  The turbine runner is rotated by this fluid flow, and the turbine shaft 11 connected to the turbine runner rotates. The stator amplifies the power of the engine 3 by converting the flow of fluid from the turbine runner so as to follow the rotation direction of the pump impeller.

  The torque converter 10 is provided with a lockup clutch (not shown), and the lockup clutch fastens the turbine runner to the front cover 10 </ b> A when oil for fastening the lockup clutch is supplied. Thereby, the motive power of the engine 3 is transmitted to the turbine shaft 11 by rotating the turbine runner from the front cover 10A without passing the fluid.

  When oil for releasing the lockup clutch is supplied to the lockup clutch, the lockup clutch pulls the turbine runner away from the front cover 10A. Thereby, the motive power of the engine 3 is transmitted to the turbine shaft 11 by rotating the turbine runner from the front cover 10A via the fluid.

  A partition wall 31 is formed in the torque converter housing 5, and the partition wall 31 partitions a space inside the torque converter housing 5 from a space inside the front case 6. The turbine shaft 11 is rotatably supported by a bearing support portion 31 a formed on the partition wall 31 via a bearing 40. The torque converter 10 of the present embodiment constitutes a rotating member of the present invention, and the turbine shaft 11 constitutes a rotating shaft of the present invention. The partition wall 31 constitutes a wall portion of the present invention.

  An oil pump 12 is accommodated in the torque converter housing 5, and the oil pump 12 is composed of, for example, a trochoid oil pump. The oil pump 12 includes a rear pump case 13 fixed to the partition wall 31 by bolts (not shown) and a front pump case 14 fastened to the rear pump case 13 by bolts (not shown).

  A pump chamber 15 is formed in an internal space between the rear pump case 13 and the front pump case 14, and an inner rotor and an outer rotor (not shown) are provided in the pump chamber 15. The inner rotor is attached to a part of the shell 10B so as to rotate integrally with the shell 10B.

  The outer rotor is provided on the radially outer side of the inner rotor, and rotates with the rotation of the inner rotor. The trochoidal oil pump 12 includes a plurality of unillustrated oil pumps that accommodate oil between the external teeth and the internal teeth by contacting the internal teeth formed on the outer rotor with the external teeth formed on the inner rotor. The working chamber is formed.

  In the oil pump 12, when the power of the engine 3 is transmitted to the inner rotor by the shell 10B, the inner rotor and the outer rotor rotate in one direction. At this time, the volume increase and the volume decrease of the working chamber continuously occur, so that oil is sucked into the working chamber from a suction port (not shown), and the oil pressurized by the working chamber is discharged from a discharge port (not shown).

  An enlarged diameter portion 11 </ b> A is formed at the rear end portion of the turbine shaft 11, and the enlarged diameter portion 11 </ b> A is formed to have a larger diameter than the front end portion and the center portion of the turbine shaft 11. An annular flywheel 16 is attached to the enlarged diameter portion 11 </ b> A, and the flywheel 16 is accommodated in the front case 6.

  A clutch 17 is accommodated in the front case 6, and the clutch 17 is attached to the flywheel 16 so as to face the flywheel 16.

  The clutch 17 is installed at the front end 21 a in the axial direction of the input shaft 21. The input shaft 21 is accommodated in the front case 6 and the rear case 7, and is rotatably supported by a partition wall 6W formed in the front case 6 on the front end side in the axial direction, and the rear end portion 21b in the axial direction is the output shaft. 22 is rotatably supported.

  The output shaft 22 faces the input shaft 21 in the axial direction of the input shaft 21. The output shaft 22 is rotatably supported by the partition wall 7C and the extension case 8 formed at the rear end portion of the rear case 7 via bearings 39A and 39B, respectively, and rotates relative to the input shaft 21.

  The clutch 17 includes a clutch disk 17A that is integrally rotatable with the input shaft 21 and is movable in the axial direction of the input shaft 21, a pressure plate 17B that presses the clutch disk 17A against the flywheel 16, and a pressure plate 17B that flies. A diaphragm spring 17C that biases the wheel 16 is provided.

  A cylindrical portion 6w is formed in the partition wall 6W of the front case 6, and the cylindrical portion 6w extends from the radially inner end of the partition wall 6W to the clutch 17 side along the axial direction of the input shaft 21.

  A release bearing 18 is provided on the outer peripheral portion of the cylindrical portion 6w. The release bearing 18 acts on the biasing force of the diaphragm spring 17C when a biasing force of a clutch lever (not shown) is applied to the axial direction of the input shaft 21. It moves to the front against this and contacts the radially inner end of the diaphragm spring 17C. On the other hand, when the urging force of the clutch lever no longer acts, the clutch lever 17C moves rearward due to the urging force of the diaphragm spring 17C, and moves away from the radially inner end of the diaphragm spring 17C.

  When the clutch lever is not operating, the release bearing 18 is separated from the radially inner end of the diaphragm spring 17C. At this time, the diaphragm spring 17C urges the pressure plate 17B to press the clutch disc 17A against the flywheel 16. As a result, the clutch 17 transmits the rotation of the crankshaft of the engine 3 to the input shaft 21.

  When the clutch lever is operated, the release bearing 18 presses the radially inner end of the diaphragm spring 17C forward. At this time, the urging of the pressure plate 17B is released, and the clutch disc 17A is separated from the flywheel 16. As a result, the clutch 17 does not transmit the rotation of the crankshaft of the engine 3 to the input shaft 21.

  Thus, the clutch 17 can transmit power or can block power between the crankshaft of the engine 3 and the input shaft 21.

  A counter shaft 23 is accommodated in the front case 6 and the rear case 7, and the counter shaft 23 is rotatably supported by the partition walls 6W and 7C. The counter shaft 23 extends in parallel with the input shaft 21 and the output shaft 22.

  The input shaft 21 is provided with a fourth speed input gear 24A, a third speed input gear 24B, a second speed input gear 24C, a first speed input gear 24D, and a reverse input gear 24E from the clutch 17 side toward the output shaft 22.

  The fourth speed input gear 24A, the third speed input gear 24B, the second speed input gear 24C, the first speed input gear 24D and the reverse input gear 24E are connected to the input shaft 21 so as to be relatively rotatable.

  A 5-speed clutch gear 22 </ b> A is provided at the front end portion of the output shaft 22, and the 5-speed clutch gear 22 </ b> A includes a dog formed on the outer peripheral portion of the output shaft 22.

  The counter shaft 23 is provided with a fourth speed counter gear 26A, a third speed counter gear 26B, a second speed counter gear 26C, a first speed counter gear 26D and a counter drive gear 26E from the clutch 17 side toward the output shaft 22.

  The 4-speed counter gear 26A, the 3-speed counter gear 26B, the 2-speed counter gear 26C, the 1-speed counter gear 26D and the counter drive gear 26E are fixed to the counter shaft 23 and cannot rotate relative to the counter shaft 23. .

  The fourth speed counter gear 26A, the third speed counter gear 26B, the second speed counter gear 26C, and the first speed counter gear 26D are the fourth speed input gear 24A, the third speed input gear 24B, and the second speed input gear 24C that constitute the same gear stage, respectively. Meshes with the first-speed input gear 24D.

  The counter drive gear 26E meshes with the counter driven gear 27, and the counter driven gear 27 is fixed to the output shaft 22 so as to rotate integrally with the output shaft 22.

The front case 6 and the rear case 7 accommodate a synchronizer 28 for the third and fourth speeds, a synchronizer 29 for the first and second speeds, and a synchronizer 30 for the reverse-5 speeds.
The third-speed / four-speed synchronization device 28 can be rotated integrally with the input shaft 21 and is movable in the axial direction of the input shaft 21. The three-speed / four-speed synchronizer 28 is a shift-and-shift via a three-speed / four-speed shift fork, a three-speed / four-speed shifter shaft, and a three-speed / four-speed shift yoke (not shown). The select shaft 42 can be moved.

  The shift-and-select shaft 42 selects the shift yoke for the third speed and the fourth speed, and moves the shift fork for the third speed and the fourth speed in the axial direction of the input shaft 21 via the shifter shaft for the third speed and the fourth speed. Then, the synchronizer 28 for the third speed and the fourth speed is moved in the axial direction of the input shaft 21.

  The 1st-2nd gear synchronizer 29 shifts via a shift fork for 1st-2nd speed (not shown), a shifter shaft 29A for 1st-2nd speed and a shift yoke for 1st-2nd speed (not shown). It can be moved by the and select shaft 42.

  The shift-and-select shaft 42 selects the shift yoke for the first speed-2 speed, and the shift fork for the first speed-2 speed is moved in the axial direction of the input shaft 21 via the shifter shaft 29A for the first speed-2 speed. If it does, the synchronizer 29 for 1st-2nd will be moved to the axial direction of the input shaft 21. FIG.

  The synchronizer 30 for reverse-5 speed is provided so as to be rotatable integrally with the input shaft 21 and movable in the axial direction of the input shaft 21. The reverse-5 speed synchronizer 30 includes a shift and select shaft 42 via a reverse-5 speed shift fork, a reverse-5 speed shifter shaft, and a reverse-5 speed shift yoke (not shown). It is movable.

  When the shift-and-select shaft 42 selects a reverse-5-speed shift yoke and moves the reverse-5-speed shift fork in the axial direction of the input shaft 21 via the reverse-5-speed shifter shaft 30A, The reverse-5 speed synchronizer 30 is moved in the axial direction of the input shaft 21.

  The third-speed / four-speed synchronization device 28 moves from the neutral position to the front side in the axial direction of the input shaft 21 to connect the fourth-speed input gear 24A to the input shaft 21 to establish the fourth forward speed. The power of the input shaft 21 is transmitted to the counter shaft 23 via the 4-speed input gear 24A and the 4-speed counter gear 26A.

  The power transmitted to the counter shaft 23 is transmitted from the counter drive gear 26E to the output shaft 22 via the counter driven gear 27. A differential device (not shown), a drive shaft, and a driving rear wheel are all connected to the output shaft 22 via a propeller shaft (not shown).

  Thereby, the power transmitted to the output shaft 22 is transmitted to the differential device via the propeller shaft, and is distributed to the left and right drive shafts by the differential device and then transmitted to the driving rear wheel. As a result, the vehicle 1 travels.

  The third-speed / four-speed synchronization device 28 moves from the neutral position to the rear side in the axial direction of the input shaft 21, thereby connecting the third-speed input gear 24B to the input shaft 21 to establish the third forward speed. The power of the input shaft 21 is transmitted to the counter shaft 23 via the third speed input gear 24B and the third speed counter gear 26B.

  The first-second-speed synchronization device 29 moves from the neutral position to the front side in the axial direction of the input shaft 21, thereby connecting the second-speed input gear 24C to the input shaft 21 to establish the second forward speed. The power of the input shaft 21 is transmitted to the counter shaft 23 via the second speed input gear 24C and the second speed counter gear 26C.

  The first-speed-second-speed synchronization device 29 moves from the neutral position to the rear side in the axial direction of the input shaft 21, thereby connecting the first-speed input gear 24D to the input shaft 21 to establish the first forward speed. The power of the input shaft 21 is transmitted to the counter shaft 23 via the first speed input gear 24D and the first speed counter gear 26D.

  The reverse-5 speed synchronizer 30 moves from the neutral position to the front side in the axial direction of the input shaft 21, thereby connecting the reverse input gear 24 </ b> E to the input shaft 21 to establish the reverse gear. Power is transmitted from the reverse input gear 24E to the counter shaft 23 via a reverse idler gear, a reverse output gear, and a first speed counter gear 26D (not shown). At this time, the counter shaft 23 rotates in the direction opposite to the rotation direction at the time of forward movement, so that the vehicle 1 is moved backward.

  The reverse-5 speed synchronizer 30 moves from the neutral position to the rear side in the axial direction of the input shaft 21 to connect the fifth speed clutch gear 22A to the input shaft 21 to establish the fifth forward speed. The power of the input shaft 21 is directly transmitted to the output shaft 22.

  A shift case 9 is provided above the front case 6, and the shift and select shaft 42 is provided inside the shift case 9. The shift and select shaft 42 extends in the vehicle width direction orthogonal to the direction in which the input shaft 21 extends.

  The shift and select shaft 42 is provided on the shift case 9 so as to be rotatable and movable in the axial direction, and is operated by a shift unit (not shown).

  The partition wall 31 on the front case 6 side of the torque converter housing 5 has an outer peripheral wall portion 31A and a bulging wall portion 31B. 3 to 5, the outer peripheral wall portion 31A is located radially outward of the bearing support portion 31a. The bulging wall portion 31B bulges from the radially inner side of the outer peripheral wall portion 31A toward the axially outer side of the turbine shaft 11 (see FIG. 2). The axially outward direction of the turbine shaft 11 is on the input shaft 21 side with respect to the outer peripheral wall portion 31A.

  That is, in the bulging wall portion 31B, the tip end portion 31b bulges toward the input shaft 21 from the partition wall 31, and a cylindrical space is formed inside. The oil pump 12 is accommodated in this cylindrical space. (See FIG. 2). A stepped portion 31c is formed in the bulging wall portion 31B, and the stepped portion 31c is curved toward the outer peripheral wall portion 31A from the radial outer end of the distal end portion 31b of the bulging wall portion 31B.

  In FIG. 2, the rear pump case 13 of the oil pump 12 is fixed to the back surface of the tip portion 31b of the bulging wall portion 31B on the torque converter 10 side by a bolt (not shown).

  In FIG. 3, a bearing support portion 31a is formed at the distal end portion 31b of the bulging wall portion 31B. The turbine shaft 11 is rotatably supported via the bearing 41 on the bearing support portion 31a. An annular rib 31C is formed at the tip 31b of the bulging wall 31B.

  The annular rib 31C is formed in an annular shape that surrounds the radially outer side of the bearing support portion 31a, and protrudes outward of the turbine shaft 11 from the tip portion 31b of the bulging wall portion 31B. The annular rib 31C of the present embodiment constitutes a reinforcing portion of the present invention.

  Oil passage bulging portions 32, 33, 34, 35, 36 formed in a boss shape are provided at the distal end portion 31b of the bulging wall portion 31B, and the oil passage bulging portion 32 extends from the oil passage bulging portion 32. An oil passage 36a is formed from the oil passage 32a inside the outlet portion 36, respectively.

  The oil passage bulging portion 33 to the oil passage bulging portion 35 are located on the inner side in the circumferential direction of the annular rib 31C, and the oil passage bulging portions 32 and 36 are oil passage bulging portions 33, respectively. To the oil passage bulging portion 35 on the outer side in the circumferential direction.

  In this embodiment, the oil passage bulging portion 33 to the oil passage bulging portion 35 constitute the inner oil passage bulging portion of the present invention, and the oil passage bulging portions 32 and 36 are located outside the present invention. An oil passage bulge is formed.

  The oil passage bulge portion 32 extends from the oil passage bulge portion 32 downward from the annular rib 31C. Specifically, the upper end portion 32b to the upper end portion 36b of the oil passage bulging portion 36 are connected to the annular rib 31C along the circumferential direction of the annular rib 31C.

  The lower end portion 32c to the lower end portion 36c of the oil passage bulge portion 36 to the oil passage bulge portion 36 are located at the same height position. As a result, the oil passage bulges 32 and 36 located outside are formed longer from the oil passage bulges 33 located inside than the oil passage bulges 35 in the vertical direction. .

  The oil passage bulging portion 36 is connected to the oil passage bulging portion 32 adjacent to the annular rib 31C in the circumferential direction. Specifically, as shown in FIG. 6, an oil passage bulging portion 32 and an oil passage bulging portion 33, an oil passage bulging portion 33 and an oil passage bulging portion 34, and an oil passage bulging portion. 34, the oil passage bulging portion 35, and the oil passage bulging portion 35 and the oil passage bulging portion 36 are connected to each other.

  The oil passage bulge portion 32 to the oil passage bulge portion 36 bulge outward from the tip end portion 31b of the bulge wall portion 31B in the axial direction of the turbine shaft 11, and the input shaft 21 is more than the outer peripheral wall portion 31A. Located on the side.

  From the oil passage bulge portion 32 to the oil passage bulge portion 36, the lower end portion 32c to the lower end portion 36c are open, and the oil passages 34a, 35 have oil passages 34a, 35a having an opening diameter of The oil passage bulges 32, 33, 36 are formed to have a diameter larger than the opening diameter of the oil passages 32a, 33a, 36a.

  In FIG. 3, the oil passage bulges 32 and 36 located on the outer side are connected to outer bosses 37 and 38, respectively. Oil passages 37a and 38a are formed inside the outer boss portions 37 and 38, and the oil passages 37a and 38a communicate with the oil passages 32a and 33a and the oil passage 36a, respectively.

  The outer boss portions 37 and 38 extend from the outer oil passage bulging portions 32 and 36 to the stepped portion 31c in the radial outside of the bearing support portion 31a, and the stepped portion and the tip portion 31b of the bulging wall portion 31B. 31c.

  In other words, the outer boss portions 37 and 38 bulge outward from the bulging wall portion 31B to the turbine shaft 11 and bulge outward from the step portion 31c in the radial direction of the bearing support portion 31a. The outer boss portions 37 and 38 extend from the outer oil passage bulge portions 32 and 36 to the joint portion 5A.

  The lower end portion of the oil passage bulging portion 35 is connected to the valve body 62 from the oil passage bulging portion 32. In FIG. 1, the valve body 62 is fastened to the lower portion of the front case 6 with a bolt (not shown), and is accommodated in a valve body chamber 63 formed by the oil pan 61 and the lower portion of the front case 6.

  The oil pan 61 is attached to the lower portion of the front case 6 with a bolt (not shown) so as to cover the front case 6 from below. Oil is stored in the oil pan 61, and the valve body 62 supplies the oil stored in the oil pan 61 from the oil passage bulging portion 33 to the oil passage bulging portion 36.

  The valve body 62 includes a regulator 62a, a lockup valve 62b, an electromagnetic solenoid (not shown), and the like.

  The oil passage 35 a of the oil passage bulging portion 35 communicates the valve body 62 and the suction port of the oil pump 12, and the oil passage 34 a of the oil passage bulging portion 34 is connected to the valve body 62 and the oil pump 12. It communicates with the discharge port.

  The oil passage 33a of the oil passage bulging portion 33 is passed through the oil passage for fastening the lockup clutch (not shown) formed in the partition wall 31 and the oil passage for fastening the lockup clutch (not shown) formed in the rear pump case 13. It communicates with an oil passage 45 (see FIG. 2) between 10B and the turbine shaft 11.

  The oil stored in the oil pan 61 is sucked into the suction port of the oil pump 12 from the valve body 62 through the oil passage 35a.

  The oil sucked into the suction port is pressurized in the working chamber of the oil pump 12 and supplied from the discharge port to the valve body 62 through the oil passage 34a. The oil supplied from the oil passage 34a to the valve body 62 is regulated by the regulator 62a.

  In the lock-up execution state, the valve body 62 is switched by the electromagnetic solenoid so that the lock-up valve 62b selects the oil passage for engaging the lock-up clutch. The oil passage 33a is introduced into the oil passage 45 through the oil passage for fastening the lockup clutch of the partition wall 31 and the oil passage for fastening the lockup clutch of the rear pump case 13. The lock-up clutch is actuated by oil introduced into the oil passage 45, and fastens the turbine runner to the front cover 10A.

  The oil passage 36 a of the oil passage bulging portion 36 is oiled through a lockup clutch release oil passage (not shown) formed in the partition wall 31 and a lockup clutch release oil passage (not shown) formed in the rear pump case 13. It communicates with the passage 11B (see FIG. 2).

  The oil passage 11 </ b> B is formed along the axial direction of the turbine shaft 11 inside the turbine shaft 11, and the front end portion is open.

  In the lockup release state, the valve body 62 is switched by the electromagnetic solenoid so that the lockup valve 62b selects the oil passage for releasing the lockup clutch. The oil passage 36a is introduced into the oil passage 11B through the oil passage for releasing the lockup clutch of the partition wall 31 and the oil passage for releasing the lockup clutch of the rear pump case 13. The lock-up clutch is actuated by oil introduced into the oil passage 11B, and pulls the turbine runner away from the front cover 10A.

  The lock-up clutch is actuated by oil introduced into the oil passage 11B, and pulls the turbine runner away from the front cover 10A.

  Thus, the oil pump 12 has a function of generating a hydraulic pressure for operating the lockup clutch, and the oil passage bulging portion 36 is provided from the oil passage bulging portion 33 provided in the torque converter housing 5 to the valve body 62. And the torque converter 10 are made to circulate oil.

  The oil passage bulge portion 32 of the oil passage bulge portion 32 is an oil return passage for returning the oil that has lubricated the bearing 41 and the like around the oil pump 12 to the oil pan 61.

  According to the automatic transmission 2 of the present embodiment, the torque converter 10 having the turbine shaft 11 is accommodated, and the torque converter housing 5 that rotatably supports the turbine shaft 11 on the bearing support portion 31 a formed on the partition wall 31 is provided.

  The partition wall 31 extends downward from the annular rib 31C so as to bulge outward from the partition wall 31 in the axial direction of the turbine shaft 11 and the annular rib 31C surrounding the bearing support portion 31a radially outward of the bearing support portion 31a. The oil passage bulge portion 36 is formed from the oil passage bulge portion 32 in which an oil passage 36a is formed from the oil passage 32a.

  Thereby, the rigidity of the partition 31 around the bearing support portion 31a can be improved by the annular rib 31C. Further, by providing the oil passage bulging portion 36 from the oil passage bulging portion 32 below the annular rib 31C, in addition to improving the rigidity of the annular rib 31C, the rigidity of the partition wall 31 below the annular rib 31C is increased. It can be improved. For this reason, the rigidity of the bearing support portion 31a can be improved, and the support rigidity of the turbine shaft 11 can be easily improved.

  Further, according to the automatic transmission 2 of the present embodiment, the oil passage bulge portion 32 to the oil passage bulge portion 36 are connected to the annular rib 31C from the upper end portion 32b to the upper end portion 36b, respectively. The oil passage bulges 36 are connected to the oil passage bulges 32 adjacent to each other in the circumferential direction of the annular rib 31C.

  As a result, the rigidity of the partition wall 31 along the circumferential direction of the annular rib 31C can be improved by the oil passage bulge portion 36 from the oil passage bulge portion 32, and the rigidity of the bearing support portion 31a in the circumferential direction can be easily achieved. It can be improved. As a result, the support rigidity of the turbine shaft 11 can be improved more effectively.

  Further, according to the automatic transmission 2 of the present embodiment, the oil passage bulging portion 36 extends from the oil passage bulging portion 32 to the inside of the annular rib 31C in the circumferential direction. The oil passage bulging portion 35 and the oil passage bulging portions 32 and 36 located outside the oil passage bulging portion 35 from the inner oil passage bulging portion 33 are provided.

  The outer oil passage bulge portions 32 and 36 are connected to the outer boss portions 37 and 38, and the outer boss portions 37 and 38 have oil passages 37a and 38a communicating with the oil passages 33a and 36a. The outer oil passage bulges 32 and 36 extend outward in the radial direction of the bearing support 31a.

  Accordingly, the rigidity of the outer oil passage bulges 32 and 36 can be improved by the outer boss parts 37 and 38, and the rigidity of the partition wall 31 along the circumferential direction of the annular rib 31 </ b> C can be increased from the oil passage bulge part 32. The oil passage bulging portion 36 can improve more effectively. As a result, the circumferential rigidity of the bearing support portion 31a can be more effectively improved, and the support rigidity of the turbine shaft 11 can be more effectively improved.

  A hydraulic sensor (not shown) is attached to the outer boss portions 37 and 38. This hydraulic sensor detects the pressure of oil flowing through the oil passages 33a and 36a. The oil pressure sensor may detect the oil pressure by being always attached to the outer boss portions 37 and 38. Alternatively, it may be attached to the outer boss portions 37 and 38 only when the oil passage is inspected.

  When a hydraulic pressure sensor is attached to the outer boss portions 37 and 38 only when the oil passage is inspected, the outer boss portions 37 and 38 are closed by a plug (not shown) except during the inspection of the oil passage.

  Further, according to the automatic transmission 2 of the present embodiment, the partition wall 31 includes the outer peripheral wall portion 31A located radially outward of the bearing support portion 31a and the turbine shaft 11 from the radially inner side of the outer peripheral wall portion 31A. An bulging wall portion 31B that bulges outward in the axial direction, and an oil passage bulging portion 36 is formed from the bearing support portion 31a, the annular rib 31C, and the oil passage bulging portion 32 of the bulging wall portion 31B. It is formed at the tip 31b in the bulging direction.

  The outer boss portions 37 and 38 are formed in a stepped portion 31c that curves from the radially outer end of the distal end portion 31b of the bulging wall portion 31B toward the outer peripheral wall portion 31A. Thereby, the rigidity of the outer boss portions 37 and 38 can be further improved by forming the outer boss portions 37 and 38 in the step portion 31c having high rigidity.

  For this reason, the rigidity of the outer oil passage bulges 32 and 36 can be more effectively improved by the highly rigid outer boss parts 37 and 38, and the rigidity of the partition wall 31 along the circumferential direction of the annular rib 31C can be improved. The passage bulge portion 32 can be improved more effectively by the oil passage bulge portion 36. As a result, the circumferential rigidity of the bearing support portion 31a can be more effectively improved, and the support rigidity of the turbine shaft 11 can be more effectively improved.

  Further, according to the automatic transmission 2 of the present embodiment, the case has the fastening portion 5B formed in the partition wall 31, and the outer boss portions 37, 38 are connected to the outer oil passage bulging portions 32, 36. It extends toward the fastening part 5B.

  Accordingly, by extending the outer boss portions 37 and 38 to the highly rigid fastening portion 5B to which the fastening portion 6B of the front case 6 is fastened, the rigidity of the outer boss portions 37 and 38 can be further improved by the fastening portion 5B.

  For this reason, the rigidity of the outer oil passage bulges 32 and 36 can be improved more effectively by the outer bosses 37 and 38 having higher rigidity, and the rigidity of the partition wall 31 along the circumferential direction of the annular rib 31C. Can be improved more effectively by the oil passage bulge portion 36 than the oil passage bulge portion 32.

  As a result, the circumferential rigidity of the bearing support portion 31a can be more effectively improved, and the support rigidity of the turbine shaft 11 can be more effectively improved. The outer boss portions 37 and 38 may be connected to the fastening portion 5B.

  In the automatic transmission 2 of the present embodiment, the rotating member is constituted by a torque converter, but the rotating member is not limited to the torque converter. In the support structure of the turbine shaft 11 of the present embodiment, the torque converter 10 is applied to the automatic transmission 2, but is not limited to the automatic transmission 2, and includes a case having an oil passage bulge. Any device can be used as long as it is a new device.

  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.

  5 ... torque converter housing (case), 5B ... fastening part (first fastening part), torque converter housing (case), 6 ... front case (other case), 6B ... fastening part (first 2 fastening portions), 10 ... torque converter (rotating member), 11 ... turbine shaft (rotating shaft), 31 ... partition wall (wall portion), 31A ... outer peripheral wall portion, 31a ... Bearing support portion, 31B ... bulging wall portion, 31b ... tip portion (tip portion in the bulging direction of the bulging wall portion), 31C ... annular rib (reinforcing portion), 31c ... step portion , 32, 36... Oil passage bulging portion (outer oil passage bulging portion), 32a, 33a, 34a, 35a, 36a... Oil passage (oil passage bulging portion oil passage), 32b , 33b, 34b, 35b, 36b ... upper end (upper end of the oil passage bulge), 33, 34, 35 ... oil passage bulge (inner oil passage bulge) Parts), 37, 38 ... outer boss portion, 37a, 38a ... oil passage (oil passage of the outer boss)

Claims (5)

A rotating shaft support structure comprising a case that accommodates a rotating member having a rotating shaft and rotatably supports the rotating shaft on a bearing support portion formed on a wall portion,
The wall portion is formed from an annular reinforcing portion that surrounds the bearing support portion radially outward of the bearing support portion, and from the reinforcement portion so as to bulge outward from the wall portion in the axial direction of the rotating shaft. A rotating shaft support structure comprising a plurality of oil passage bulges extending downward and having oil passages formed therein. Each of the plurality of oil passage bulges has an upper end connected to the reinforcement,
2. The support structure for a rotating shaft according to claim 1, wherein the plurality of oil passage bulging portions are connected to oil passage bulging portions adjacent in the circumferential direction of the reinforcing portion. The plurality of oil passage bulging portions are located on the outer side in the circumferential direction with respect to the inner oil passage bulging portion and the inner oil passage bulging portion located on the inner side in the circumferential direction of the reinforcing portion. A bulging portion for the outer oil passage,
The bulging portion for the outer oil passage is connected to an outer boss portion provided on the wall portion,
The outer boss has an oil passage communicating with the oil passage of the outer oil passage bulging portion, and extends from the outer oil passage bulging portion outward in the radial direction of the bearing support portion. The rotating shaft support structure according to claim 1 or 2, wherein the support structure is a rotating shaft support structure. The wall portion includes an outer peripheral wall portion positioned radially outward of the bearing support portion, and a bulging wall portion bulging outward from the radial inner side of the outer peripheral wall portion in the axial direction of the rotating shaft. The bearing support portion, the reinforcing portion, and the plurality of oil passage bulge portions are formed at the distal end portion of the bulge wall portion in the bulge direction,
The said outer boss | hub part is formed in the level | step-difference part curved toward the said outer peripheral wall part from the outer end of the radial direction of the front-end | tip part of the bulging direction of the said bulging wall part. The support structure of the rotating shaft as described. The case has a first fastening portion formed on the wall portion, and a second fastening portion of another case is fastened to the first fastening portion,
The rotating shaft support structure according to claim 3 or 4, wherein the outer boss portion extends from the bulging portion for the outer oil passage toward the first fastening portion.

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