JP2005024072A - Lubricating device of transmission mechanism for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating device, restraining decrease in quantity of lubricating oil supplied to a part needing lubrication. <P>SOLUTION: In this lubricating device of a transmission mechanism for a vehicle, a guide member in which lubricating oil adheres to the lower end thereof to flow is formed extending in a predetermined direction in a casing 8. Since an oil carrying rib 38 and an oil carrying rib 39 are formed substantially parallel to each other, acceleration is caused vertically to the oil carrying rib 38 and the oil carrying rib 39, whereby when the acceleration causes the pressure to the lubricating oil, the lubricating oil can be held by surface tension in the oil carrying rib 39 formed substantially parallel to the oil carrying rib 38 or between the oil carrying rib 38 and the oil carrying rib 39, thereby restraining decrease in quantity of lubricating oil supplied to a part needing lubrication. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an apparatus for lubricating a vehicle transmission mechanism provided in a power transmission path of a vehicle.

  Conventionally, a scraping method is known as one of the methods of lubricating and cooling a heat generating part in a vehicle power transmission device with oil. An example of the scraping method is described in Patent Document 1. In the lubrication apparatus described in Patent Document 1, a through hole for communicating the front chamber and the rear chamber is provided in a partition wall at the rear end inside the transmission case. Further, a front rib is continuously provided on the ceiling surface of the transmission case to the rear end surface of the through hole for supplying the lubricating oil adhering to the ceiling surface to the rear by scraping the gear, and further on the ceiling surface of the rear cover. A rear rib continuously connected to the rear portion of the front rib is provided.

And in the lubricating device described in patent document 1, the lubricating oil adhering to the ceiling surface of the said transmission case by the gear scraping is transmitted to the rear chamber side through the through hole through the lower end surfaces of the front rib and the rear rib. Supply and supply lubricating oil to oil seal etc. Other examples of the lubrication device are described in Patent Document 2 and Patent Document 3.
JP 2002-221273 A (paragraph number 0006, paragraph number 0018, paragraph number 0033, FIG. 1) JP-A-11-218213 (summary, FIG. 2) Japanese Patent Laid-Open No. 11-247777 (summary, FIG. 1)

  However, in the lubricating device described in Patent Document 1, for example, acceleration in the front-rear direction occurs when the vehicle accelerates or decelerates, and acceleration in the left-right direction occurs when turning, for example. Such various accelerations act as pressure on the lubricating oil. Therefore, there is a problem that the lubricating oil flowing with the rib as a guide member flows over the rib and the lubricating oil supplied to the rear chamber and the oil seal to be guided by the rib is reduced.

  An object of the present invention is to solve the above-described problems, and an object of the present invention is to provide a lubrication apparatus capable of suppressing a decrease in the amount of lubricating oil supplied to a site requiring lubrication.

  In order to achieve the above object, according to the first aspect of the present invention, a guide member for causing a lubricant to flow by adhering to the tip thereof is formed extending in a predetermined direction inside the casing to lubricate the lubricant. In the lubricating device for a vehicle transmission mechanism to be supplied to the vehicle, the plurality of guide members are formed substantially parallel to each other.

  According to the first aspect of the present invention, since a plurality of guide members are formed in the casing so as to extend in a predetermined direction, acceleration occurs perpendicularly to the guide members, and pressure is applied to the lubricating oil. In this case, even if the lubricating oil gets over one guide member, the other guide member holds the lubricating oil by surface tension.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the plurality of guide members are formed in parallel with each other at a predetermined interval. .

  According to the second aspect of the invention, in addition to the action of the first aspect, even if the lubricating oil climbs over the one guide member, the other guide member formed parallel to the one guide member, or The lubricating oil is held by the surface tension between the one guide member and the other guide member.

  In addition to the structure of claim 1 or 2, the invention of claim 3 is provided with a guide member that guides the lubricating oil scraped up by a predetermined rotating member in a plurality of directions and branches in the plurality of directions. A plurality of guide members are provided in a passage of the lubricating oil branched in one direction among the plurality of directions. This is a lubricating device for a transmission mechanism for a vehicle.

  According to the invention of claim 3, in addition to the action of claim 1 or 2, the lubricating oil scraped up by the rotating member is branched in a plurality of directions by the guiding member, and a part of the lubricating oil branched in one direction Is guided to the guide member. Then, the branched lubricating oil is supplied to the same lubricating oil receiver. Therefore, the amount of lubricating oil stored in the casing is adjusted by the lubricating oil receiving portion regardless of the rotational speed of the rotating member.

  According to a fourth aspect of the present invention, there is provided a lubricating mechanism for a vehicle transmission mechanism in which a guide member for adhering and flowing lubricating oil to the tip thereof extends in a predetermined direction inside the casing and supplies the lubricating oil to a portion requiring lubrication. In the apparatus, a plurality of the guide members are formed adjacent to each other, and are a lubricating device for a transmission mechanism for a vehicle.

  According to the fourth aspect of the present invention, since a plurality of guide members are formed in the casing so as to extend in a predetermined direction, acceleration occurs perpendicularly to the guide members, and pressure is applied to the lubricating oil. In this case, even if the lubricating oil climbs over one guide member, the lubricating oil is held by the surface tension on another guide member formed adjacent to the one guide member.

  As described above, according to the first aspect of the present invention, since a plurality of guide members are formed in the casing so as to extend in a predetermined direction, acceleration occurs perpendicularly to the guide members, and the lubricating oil When the lubricant acts on one guide member, even if the lubricant climbs over one guide member, the other guide members formed substantially parallel to one guide member may cause the lubricant to flow. Can be held by surface tension. Therefore, it is possible to suppress a decrease in the amount of lubricating oil supplied to the site requiring lubrication.

  According to a second aspect of the invention, in addition to the effect of the first aspect, in addition to the other guide member, the other guide member and the other member when the lubricating oil gets over the one guide member. The lubricating oil can also be held between the guide members by surface tension. Therefore, it is possible to more efficiently suppress a decrease in the amount of lubricating oil supplied to the site requiring lubrication.

  According to the invention of claim 3, in addition to the effect of claim 1 or 2, the lubricating oil scraped up by the rotating member is branched by the guide member in accordance with the rotational speed of the rotating member. , Can be guided to the guide member. And the lubricating oil branched by the said guide member can be supplied to the same lubricating oil receiving part. Therefore, the amount of lubricating oil stored in the casing can be adjusted by the lubricating oil receiving portion regardless of the rotational speed of the rotating member.

  According to the invention of claim 4, since a plurality of guide members are formed in the casing so as to extend in a predetermined direction, acceleration is generated perpendicularly to the guide members, and the lubricating oil is When acting as pressure, even if the lubricating oil gets over one guiding member, the lubricating oil can be held by surface tension by another guiding member formed adjacent to one guiding member. . Therefore, it is possible to suppress a decrease in the amount of lubricating oil supplied to the site requiring lubrication.

  Next, the present invention will be specifically described with reference to the drawings. First, a power train of a vehicle to which the present invention can be applied and a control system of the vehicle are shown in FIG. FIG. 5 is a skeleton diagram showing the power train of the vehicle Ve according to the embodiment of the present invention. The power train of the vehicle Ve includes an engine 1, a first motor / generator 2, a second motor / generator 3, a differential 4, a power distribution mechanism 5, a drive wheel 6, and the like. The power train of FIG. 5 is based on the power train of an FF vehicle (front engine / front wheel drive vehicle).

  In short, the engine 1 is a heat engine that generates power by burning fuel, and examples thereof include a gasoline engine, a diesel engine, and a natural gas engine. The first motor / generator 2 mainly generates power by receiving torque from the engine 1 and rotating. The second motor / generator 3 is a device for assisting (assisting) driving torque or braking force. When assisting driving torque, the second motor / generator 3 is supplied with electric power and functions as an electric motor, and when assisting braking force. The generator is rotated by torque transmitted from the drive wheel 6 side to function as a generator that generates electric power. The power distribution mechanism 5 is coupled to the drive wheels 6 so as to be able to transmit power via a differential 4.

  Next, an example of the lubricating device of the present invention including the differential 4 will be described. FIG. 1 is a view showing a case where the lubricating device of the present invention is applied to a power transmission device for a vehicle, specifically, a transaxle 7. In addition, the arrow in FIG. 1 has shown the flow of the lubricating oil mentioned later. The transaxle 7 has a casing 8, and the casing 8 is made of a metal material such as an aluminum alloy or cast iron. As shown in FIG. 4, a main shaft 9, a counter shaft 10, and a drive shaft 11 are provided inside the casing 8. The rotation axis (not shown) of the main shaft 9, the rotation axis (not shown) of the counter shaft 10, and the rotation axis B1 of the drive shaft 11 are arranged in parallel to each other and substantially horizontally. Yes. Further, in the height direction of the vehicle, the rotation axis of the main shaft 9 is disposed at a position lower than the rotation axis of the counter shaft 10, and the rotation axis B 1 of the drive shaft 11 is lower than the rotation axis of the main shaft 9. Is arranged. The rotation axis B1 is provided in the width direction of the vehicle Ve.

  On the other hand, a rotating shaft (not shown) of a driving force source is connected to the main shaft 9 so that power can be transmitted. A gear 12 is attached to the main shaft 9, and gears 13 and 14 are attached to the counter shaft 10. A ring gear 15 that rotates about the rotation axis B1 is provided. And the gear 12 and the gear 13 are meshed, and the gear 14 and the ring gear 15 are meshed. The main shaft 9 is provided with a speed change mechanism (not shown) composed of various gears (for example, planetary gears). An oil sump A1 is formed inside the casing 8, specifically, at the bottom of the casing 8, and a part of the ring gear 15 is immersed in the oil sump A1. The other gear and the rotating member are not immersed in the oil sump A1. Further, an oil receiving portion 16 is provided inside the casing 8, specifically, above the gear 12.

  A part of the inner wall of the casing 8, specifically, an inner wall formed on the upper portion of the counter shaft 10, is a straight portion (flat portion) 19 that extends substantially horizontally and linearly, and a straight portion 19. And a circular arc portion 20 that is continuous. The arc portion 20 is formed around the rotation axis of the counter shaft 10. Further, the arc portion 20 is displaced to the lower side as the arc portion 20 moves away from the straight portion 19.

  A substantially horizontal guide surface 22 is formed inside the casing 8 and below the straight line portion 19. A branch rib 43 having a triangular side surface is provided on the ring gear 15. The branch rib 43 has a guide surface 24 that is substantially parallel to the guide surface 22 and a guide surface 23 that faces the outer periphery of the ring gear 15.

  Further, an oil supply path K <b> 2 is formed between the guide surface 23 and the arc portion 20. A wall portion 26 is formed continuously with the guide surface 22, and an outer wall 27 of the oil receiving portion 16 is formed in parallel with the wall portion 26. An oil supply path K <b> 1 is formed between the outer wall 27 and the wall portion 26 above the gear 12. The oil supply path K1 and the oil supply path K2 are arranged in parallel to each other, and the oil supply paths K1 and K2 are both in communication with the same oil receiving portion 16.

  A ring gear 15 is attached to a differential case 28 constituting a part of the differential 4. The differential case 28 is rotatably held by a bearing 32 inside the casing 8. The drive shaft 11 is supported by the differential case 28. The differential case 28 also rotates about the rotation axis B1. Further, a shaft hole 29 is formed in the casing 8, and the drive shaft 11 is inserted into the shaft hole 29. An annular oil seal 33 is attached to the shaft hole 29. The seal lip of the oil seal 33 contacts the drive shaft 11 to form an annular seal surface.

  Further, a guide surface 34 is formed inside the casing 8 and on a part of the inner wall of the casing 8, specifically, above the differential case 28. As the guide surface 34 approaches the shaft hole 29 side from the ring gear 15 side, the guide surface 34 is inclined in a direction approaching the rotation axis B1. Further, the guide surface 34 is continuous with the rear end surface 35. The rear end surface 35 is disposed above the drive shaft 11, and the rear end surface 35 has a planar shape orthogonal to the rotation axis B1.

  A cylindrical boss portion 36 is further formed below the rear end surface 35. The upper end surface 36 </ b> A of the boss portion 36 is continuous with the rear end surface 35. An oil passage 37 penetrating the boss portion 36 is formed. The oil passage 37 is opened in an upper end surface (plane) 36A and penetrates the boss portion 36 substantially vertically. Further, the upper end surface 36 </ b> A is inclined toward the oil passage 37. The bearing 32 is fitted and fixed in the boss portion 36.

  An oil direction changing rib 44, an oil carrying rib 38, and an oil carrying rib 39 are formed on the inner surface of the casing 8. The oil direction changing rib 44 is formed above the ring gear 15 and is elongated in the front and rear direction of the vehicle as shown in FIG. The oil direction changing rib 44 is inclined so as to become lower as it goes forward of the vehicle. The oil carrying ribs 38 and the oil carrying ribs 39 are elongated in a straight line along the width direction of the vehicle Ve. In other words, the oil carrying rib 38 and the oil carrying rib 39 have a shape having no inflection point. Furthermore, the oil transport rib 38 and the oil transport rib 39 are arranged at predetermined intervals at different positions in the front-rear direction of the vehicle Ve, that is, at different positions in the direction in which acceleration acts on the vehicle Ve. In this example, the oil carrying ribs 38 and 39 are arranged substantially parallel to each other adjacent to each other. Specifically, the oil carrying ribs 38 and 39 are slightly inclined in the longitudinal direction of the mutual oil carrying ribs 38 and 39 and are arranged in a square shape. In the present invention, “substantially parallel” includes the case where the oil carrying ribs, that is, the guide members are arranged in parallel, and the case where the guide members are arranged substantially in parallel. It is. Further, “adjacent” in the present invention includes a state in which the guide members are disposed adjacent to each other, and includes a state in which at least a part of the guide members are disposed adjacent to each other. The oil transport rib 39 is provided in front of the oil transport rib 38 in the front-rear direction of the vehicle Ve. Further, the front end of the oil direction change rib 44 and the upper end of the oil transport rib 39 are continuous in the vehicle front-rear direction. Further, the oil carrying rib 38 and the oil carrying rib 39 are formed so as to protrude downward from the guide surface 34. The protruding lower end of the oil carrying rib 38 is a lower end portion 38A, and the lower end of the oil carrying rib 39 is a lower end portion 39A. Further, as shown in FIG. 1, an oil passage 37 is disposed below a position corresponding to the oil transport rib 39 in the longitudinal direction of the vehicle.

  Furthermore, the oil passage 37 is provided behind the rotation axis B1 in the front-rear direction of the vehicle. The oil passage 37 is disposed between the rear end surface 35 and the ring gear 15 in the direction of the rotation axis B1. An oil carrying rib 45 is formed below the opening 40 at the lower end of the oil passage 37. The oil carrying rib 45 is the casing 8 and is formed by projecting a part of the periphery of the drive shaft 11 in the radial direction of the drive shaft 11. The oil carrying rib 45 is inclined toward the rotation axis B1.

  Further, an oil weir 42 is formed between the oil seal 33 and the bearing 32 in the direction parallel to the rotation axis B1, as shown in FIGS. An oil passage 37 is disposed between the oil seal 33 and the bearing 32 in a direction parallel to the rotation axis B1. Further, the oil weir 42 is disposed on the side of the bearing 32 relative to the oil passage 37 or substantially at the same position as the oil passage 37 in the direction parallel to the rotation axis B1. The oil weir 42 protrudes from the boss portion 26 toward the drive shaft 11. Specifically, as shown in FIG. 1, it is formed in an arc shape centered on the rotation axis B1. The oil weir 42 is not in contact with the drive shaft 11. Further, the radius of the arc-shaped portion of the oil weir 42 around the rotation axis B <b> 1 is larger than the radius (inner diameter) of the seal lip in the oil seal 33. That is, as shown in FIG. 3, the lowest position E1 of the tip (free end) of the oil weir 42 is disposed below the lowest position E2 of the seal surface. Depending on the shaft diameter of the drive shaft 11 facing the oil weir 42, the radius of the arc-shaped portion of the oil weir 42 may be smaller than the radius (inner diameter) of the seal lip. Further, it may be arranged above the lowest part E2. Further, the lowest position E1 and the lowest position E2 may be arranged at substantially the same position in the height direction. An oil sump D1 is formed between the oil seal 33 and the oil weir 42, and as shown in FIG. 2, the oil sump D1 and the oil sump A1 are arranged at different positions in the axial direction of the rotation axis B1. .

  Next, the torque transmission action from the driving force source to the wheels will be described. The torque transmitted from the driving force source to the main shaft 9 is transmitted to the counter shaft 10 via the gear 12 and the gear 13. The torque of the counter shaft 10 is transmitted to the drive shaft 11 via the gear 14 and the ring gear 15. Next, the torque of the drive shaft 11 is transmitted to the drive wheels 6. With such torque transmission, the main shaft 9 rotates counterclockwise in FIG. 4, the counter shaft 10 rotates clockwise, and the ring gear 15 rotates counterclockwise. At this time, the rotational speed of the ring gear 15 changes according to the rotational speed of the main shaft 9 or the gear ratio of the transmission mechanism. The rotation speed of the ring gear 15 is lower than that of the gear 12.

  Since the ring gear 15 is immersed in the oil reservoir A1, the ring gear 15 rotates in a state where the oil adheres to the outer periphery of the ring gear 15 and the oil is held by the tooth gap. At this time, when the rotation speed of the ring gear 15 is less than a predetermined rotation speed (for example, low-speed rotation), the centrifugal force due to the rotation of the ring gear 15 is weak, so that the oil is located above the meshing portion of the ring gear 15 and the gear 14. It will not be skipped. That is, the oil adhering to the ring gear 15 is transferred below the branch rib 43. However, since the centrifugal force is stronger than the gravity of the oil on the outer periphery of the ring gear 15 below the meshing portion and on the left side of the meshing portion in FIG. 5, the oil is transferred from the ring gear 15 to the gear 12. Be blown towards.

  In this way, when the oil adheres to the gear 12, the oil is held by the tooth groove of the gear 12. And since the rotational speed of the gear 12 is higher than the rotational speed of the ring gear 15, the oil adhering to the gear 12 is blown upward by the centrifugal force. Most of the oil away from the gear 12 passes through the oil supply path K1 and is supplied to the oil receiver 16. The oil supplied to the oil receiving portion 16 passes through the lubrication hole 17 and is supplied mainly to the meshing portion of the gears constituting the transmission mechanism, and lubricates and cools the meshing portion of the gears. The oil having lubricated and cooled each part as described above returns to the oil sump A1 again.

  On the other hand, when the rotation speed of the ring gear 15 is equal to or higher than a predetermined rotation speed (for example, medium speed rotation, high speed rotation), the oil is blown upward from the ring gear 15 by the centrifugal force generated by the rotation of the ring gear 15. It rises through the vicinity of the inclined surface of the branch rib 43. Most of the skipped oil passes through the oil supply path K2, reaches the guide surface 22, and further moves toward the left side in FIG. This oil is supplied to the oil receiver 16 by inertia force. The oil supplied to the oil receiving portion 16 passes through the lubrication hole 17, lubricates and cools each portion, and returns to the oil sump A1 again.

  On the other hand, a part of the oil blown by the centrifugal force due to the rotation of the ring gear 15 adheres to the oil direction changing rib 44. The part of the oil moves along the oil direction changing rib 44 and reaches the guide surface 34. The guide surface 34 is inclined toward the drive shaft 11. Therefore, the part of the oil travels through the oil direction change rib 44 formed on the guide surface 34 and adheres to the lower end portion 38 </ b> A of the oil transport rib 38 and the lower end portion 39 </ b> A of the oil transport rib 39. And, when the oil is moving along the oil conveying rib 39 in the lower end portion 39A, acceleration occurs perpendicularly to the longitudinal direction of the oil conveying rib 39 and acts as pressure on the oil. Even if the oil climbs over the oil transport rib 38, it contacts an oil transport rib 39 formed adjacent to the oil transport rib 38 in parallel with each other, and at least one of the oil transport ribs 38, 39 or the oil transport rib. It is held by the surface tension between the rib 38 and the oil conveying rib 39, moves downward, and moves to the upper end surface 36A of the boss portion 36 via the rear end surface 35. Therefore, the oil enters the oil passage 37 and falls from the opening 40 and is received by the oil conveying rib 45, and the oil flows along the inclination of the oil conveying rib 45. Part of this oil falls between the oil weir 42 and the oil seal 33 to form the oil sump D1, and the other flows into the oil sump A1. When the amount of oil in the oil reservoir D1 exceeds a predetermined level, the contact portion between the drive shaft 11 and the oil seal 33 is lubricated and cooled. When the liquid level of the oil sump D1 rises, the oil in the oil sump D1 passes over the oil weir 42 and flows into the oil sump A1. When no acceleration is generated perpendicular to the longitudinal direction of the oil transport rib 39, the oil attached to the lower end portion 39 </ b> A of the oil transport rib 39 moves along the oil transport rib 39 and moves from the oil passage 37 to the oil. Supplyed to the reservoir D1, the contact portion between the drive shaft 11 and the oil seal 33 is lubricated and cooled.

  As described above, in this embodiment, since the oil supply path is formed by the oil transport rib 38 and the oil transport rib 39, when acceleration occurs in the forward direction of the vehicle Ve, or the vehicle Ve. Even when the oil travels on an uphill road, pressure is applied to the oil that has been transmitted through the oil transport rib 38, and even if the oil gets over the oil transport rib 38, the oil is disposed substantially parallel to the oil transport rib 38. The oil comes into contact with the oil carrying rib 39, and is held by the surface tension between the oil carrying rib 39 or between the oil carrying ribs 38, 39, so that the oil movement distance is long in the rotation axis B1. However, the oil can be efficiently supplied to the oil reservoir D1 via the oil passage 37.

  In addition, when acceleration occurs in the backward direction of the vehicle Ve or when the vehicle Ve travels on a downhill road, pressure is generated in the oil that has been transmitted through the ribs of the oil transport ribs 39, and the oil transport ribs 39 are overcome. Even if the oil is in contact with the oil conveying ribs 38 arranged in parallel to the oil conveying ribs 39, the oil is held by the surface tension between the oil conveying ribs 38 or between the oil conveying ribs 38, 39. Is done. As a result, oil can be efficiently supplied to the oil reservoir D1 via the oil passage 37. Furthermore, even when the vehicle Ve is affected by gravity in the front-rear direction, the oil transport ribs 38 and 39 can efficiently supply oil to the oil reservoir D1.

  In addition to the above effects, the oil carrying ribs 38 and 39 are formed in a straight line, so there is no inflection point. For this reason, it is possible to suppress “the oil moving direction is changed and the oil is dropped from the oil transport ribs 38, 39”. growing. Further, since the upper end surface 36A is inclined toward the oil passage 37, oil can be supplied to the oil sump D1 more efficiently. Further, by storing the oil in the oil reservoir D1, the portion above the oil reservoir A1 can be lubricated. Further, even if the oil stored in the oil reservoir A1 by the pump action of the bearing 32 is suppressed from flowing into the oil reservoir D1, the oil is supplied to the oil reservoir D1 by the transfer function of the oil transport ribs 38 and 39. can do. The oil conveying ribs 38 and 39 are not limited to the above-described linear shape as long as the oil can be prevented from falling off. May be.

  Further, since the oil carrying rib 38 and the oil carrying rib 39 are formed, the rigidity of the casing 8 can be improved. As a result, the vibration of the casing 8 is suppressed.

  Further, the oil scraped up by the ring gear 15 from the oil sump A1 is branched in two directions by the branching rib 43 in accordance with the rotational speed of the ring gear 15, and a part of the oil branched in one direction is supplied to the oil supply passage. It can be guided to the oil receiving part 16 via K2. And the oil branched in the other direction can be supplied to the same oil receiving part 16 via the oil supply path K1. Therefore, the oil receiving portion 16 can suppress an increase in the amount of oil stored in the bottom portion of the casing 8 regardless of the rotational speed of the ring gear 15. As a result, since the oil level can be lowered, the stirring loss of power transmitted to the ring gear 15 can be reduced. Moreover, the lubricating oil required part can be lubricated with a small amount of oil.

  In addition, the oil conveyance ribs 38 and 39 in said example can also be provided in several places where the width direction of the vehicle Ve differs. When the oil conveying ribs are provided at different positions in the width direction of the vehicle Ve, even if acceleration from the lateral direction with respect to the vehicle Ve occurs, the oil conveying ribs or the oil conveying ribs are held by surface tension. Do not fall while moving to the lubrication required part. As a result, it is possible to efficiently supply oil to the site requiring lubrication. Further, even when a plurality of lubrication-needed portions are provided and the oil moving distance is long, the oil can be supplied efficiently. In the above example, the two oil carrying ribs 38 and 39 are provided substantially in parallel as the guide member. However, three or more guide members of the present invention may be provided.

  In this embodiment, the oil supply path is branched into two paths. However, in the lubricating device of the present invention, the oil supply path may be branched into three or more paths. Moreover, the guide member in this invention should just be provided with at least one part of the guide member in several different places in the direction where an acceleration acts.

  Further, the target vehicle in the present invention is not limited to a so-called FF vehicle, and the present invention can also be applied to an FR vehicle (front engine / rear drive vehicle; engine front and rear wheel drive vehicle).

  Here, the correspondence between the configuration of this embodiment and the configuration of the present invention will be described. The oil transport rib 38 and the oil transport rib 39 correspond to a plurality of guide members of the present invention, and the ring gear 15 is the rotation of the present invention. It corresponds to a member. Further, the contact portion between the drive shaft 11 and the oil seal 33 corresponds to a portion requiring lubrication of the present invention, the oil receiving portion 16 corresponds to the lubricating oil receiving portion of the present invention, and the lower end portions 38A and 39A are guides of the present invention. The oil supply path K2 corresponds to the leading end of the member, the branched lubricating oil passage of the present invention, and the branch rib 43 corresponds to the guiding member of the present invention.

  According to the present invention, a guide member for adhering and flowing the lubricating oil to the tip thereof is formed to extend in a predetermined direction inside the casing, and the transmission for the vehicle supplies the lubricating oil to a portion requiring lubrication by the guide member. It is applicable to the lubrication device of the mechanism. Therefore, it can be used in industries related to vehicle manufacturing.

It is a front view which shows a part of transaxle to which the lubricating device of this invention is applied. It is a side view which shows a part of lubricating device of FIG. FIG. 3 is a partially enlarged view of the lubricating device of FIG. 2. FIG. 4 is a side view of FIG. 3. It is the schematic which shows the lubrication apparatus of FIG. 1 simply. 1 is a power train of a vehicle equipped with a transaxle to which the present invention is applied.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 8 ... Casing, 11 ... Drive shaft, 15 ... Ring gear, 16 ... Oil receiving part, 33 ... Oil seal, 38, 39, 45 ... Oil conveyance rib, 38A, 39A ... Lower end part, 43 ... Branch rib

Claims (4)

In the lubricating device of the transmission mechanism for a vehicle, the guide member that causes the lubricating oil to adhere to the tip and flow is formed extending in a predetermined direction inside the casing and supplies the lubricating oil to a portion requiring lubrication.
A lubricating device for a transmission mechanism for a vehicle, wherein the plurality of guide members are formed substantially parallel to each other.   The lubricating device for a transmission mechanism for a vehicle according to claim 1, wherein the plurality of guide members are formed in parallel to each other at a predetermined interval.   A guide member is provided for branching and guiding the lubricating oil scraped up by a predetermined rotating member in a plurality of directions, and a single lubricating oil receiving portion for supplying the lubricating oil branched in the plurality of directions is provided. The lubricating mechanism for a vehicle transmission mechanism according to claim 1, wherein the plurality of guide members are provided in a lubricating oil passage branched in one of the plurality of directions. apparatus. In the lubricating device of the transmission mechanism for a vehicle, the guide member that causes the lubricating oil to adhere to the tip and flow is formed extending in a predetermined direction inside the casing and supplies the lubricating oil to a portion requiring lubrication.
A lubricating device for a transmission mechanism for a vehicle, wherein the plurality of guide members are formed adjacent to each other.

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