JP2007138975A - Lubrication mechanism of planetary gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubrication mechanism of a planetary gear device for checking seizure by properly supplying lubricating oil even when towing a vehicle with a simple structure. <P>SOLUTION: Though the lubricating oil is required in response to rotation by rotating the planetary gear device 16 of a transmission 10 from the driving wheel side of the vehicle when towing the vehicle by arranging an annular oil retaining groove 74 in the peripheral direction on an inner peripheral surface of washers 62 and 64, since the lubricating oil is properly supplied in the planetary gear device 16 from the annular oil retaining groove 74, the seizure of the planetary gear device 16 prevented. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a planetary gear device lubrication mechanism provided in a vehicle drive device.

  2. Description of the Related Art Conventionally, a plurality of planetary gear devices are provided in an automatic transmission for a vehicle, and a plurality of shift speeds are established by a connection relationship between a sun gear, a carrier, and a ring gear constituting the planetary gear device. This planetary gear device is provided with a pinion gear rotatably supported by a pinion shaft held by a carrier via a bearing, and this pinion gear is rotated at a high speed especially during driving of the vehicle. For this reason, frictional heat is generated by this high-speed rotation. In order to prevent seizure of bearings and the like due to this frictional heat, there are various lubricating mechanisms that efficiently supply lubricating oil functioning as a cooling liquid into the planetary gear unit. Has been proposed.

  For example, in a conventional planetary gear unit lubrication mechanism, a hole is drilled in the pinion shaft axis, and a lubricating oil hole communicating from the hole to the outer peripheral surface of the piston shaft is provided. There is a type in which oil is discharged from an opening portion of a lubricating oil hole provided on an outer peripheral surface of the pinion shaft through an axial hole of the pinion shaft, and lubricates a bearing or the like.

  In such a planetary gear unit lubrication mechanism, lubricating oil is effectively supplied when the vehicle is driven. For example, when the vehicle is towed, the engine does not operate, so the oil pump is also the same. The lubrication oil supply stops. Further, when the vehicle is towed, the planetary gear device is rotated from the drive wheel side of the vehicle, but since the lubricating oil is not supplied, in the worst case, the planetary gear device may be seized.

  In order to solve this problem, in Patent Document 1, a lubricating oil storage space is provided inside the carrier of the planetary gear device, and when the vehicle is towed, the lubricating oil stored in the storage space is supplied into the planetary gear device for a certain period of time. The technology is disclosed. However, the lubrication mechanism configured as described above including Patent Document 1 performs drilling on the pinion shaft, and the assembly of the pinion shaft is restricted so that the opening of the lubricating oil hole faces radially outward. There is a problem that the structure of the planetary gear device becomes complicated and the production cost increases.

  On the other hand, in Patent Document 2, a notch extending from the inner peripheral surface to the outer peripheral surface of the washer is provided, and the lubricating oil is supplied through the notch, so that the structure is simpler and more productive than the above-described lubricating mechanism. A planetary gear unit lubrication mechanism with improved performance is disclosed. However, since the lubricating oil is not supplied when the vehicle is towed, the planetary gear device may be seized, which is not suitable for towing the vehicle. Further, in Patent Document 3, although an oil sump space is provided between the washer and the pinion shaft, for example, even when the vehicle is towed after being left for a long time, the oil is stably stored. There is a problem that it is not suitable when the vehicle is towed, as in Patent Document 2, instead of such an oil sump space.

Utility Model Registration No. 2586607 JP 2001-124157 A Japanese Utility Model 5-69436

  The present invention has been made in the background of the above circumstances, and its object is that the structure is simple, and seizure can be achieved by appropriately supplying lubricating oil even when the vehicle is towed. Provided is a planetary gear unit lubrication mechanism to be prevented.

  In order to achieve the above object, the gist of the invention according to claim 1 is that: (a) a planetary gear device carrier, a pinion shaft held by the carrier, and the pinion shaft rotating through a bearing; A planetary gear device for a vehicle drive device, comprising: a pinion gear supported in a possible manner; and a washer fitted to the pinion shaft in a state of being interposed between the pinion gear and the carrier. ) A circumferential annular oil reservoir groove is provided on the inner peripheral surface of the washer.

  The gist of the invention according to claim 2 is that in the lubrication mechanism of the planetary gear device according to claim 1, the annular groove is constituted by two washers, and each of the inner peripheral surfaces of the washers is provided. An annular notch is provided on one end side, and the annular oil reservoir groove is formed by overlapping surfaces of the two washers on which the notch is provided.

  According to a third aspect of the present invention, there is provided a lubricating mechanism for a planetary gear device according to the second aspect, wherein the two washers are made of different metals. .

  According to a fourth aspect of the present invention, there is provided a lubricating mechanism for a planetary gear device according to any one of the first to third aspects, wherein (a) a hole for holding the pinion shaft of the carrier is provided. A first lubricating oil hole penetrating in the thickness direction is provided on the outer peripheral side of the inner peripheral surface with the carrier as a rotation center to supply lubricating oil to the bearing, and (b) on the inner peripheral surface of the washer. Is provided with a second lubricating oil hole penetrating in the thickness direction in order to supply the lubricating oil supplied from the first lubricating oil hole of the carrier to the bearing, and (c) on the pinion gear side of the carrier, On the opposite surface is provided an annular oil receiving plate that communicates with the annular oil reservoir groove through the first lubricating oil hole and forms an annular oil receiving groove that opens to the inner peripheral side. It is characterized by being.

  According to the planetary gear unit lubrication mechanism of the first aspect, when the vehicle is towed, the planetary gear unit of the transmission is rotated from the drive wheel side of the vehicle, and the lubricating oil is required along with the rotation. Since the lubricating oil is appropriately supplied into the planetary gear device from the annular oil reservoir groove, seizure of the planetary gear device is prevented.

  According to the lubrication mechanism of the planetary gear device according to claim 2, in addition to the above-described effects, the oil reservoir groove is configured by two washers, thereby facilitating the processing of the oil reservoir groove and improving the productivity. Will improve. Further, the pinion gear and one washer, one washer and the other washer, and the other washer and the carrier are in contact with each other and rotate relative to each other, but each member is compared with the case where only one washer is provided. Since the relative rotational speed decreases, wear and heat generation between the members are suppressed, and the durability of the planetary gear device is improved.

  Further, according to the lubricating mechanism of the planetary gear device of claim 3, the two washers are made of different metal materials, so that the washer on the side in contact with the pinion gear is, for example, a steel material in addition to the above-described effects. Therefore, the durability of the planetary gear device can be further improved.

  According to the lubricating mechanism of the planetary gear device of claim 4, the lubricating oil blown off by the centrifugal force is transmitted to the planet through the first lubricating oil hole and the second lubricating oil hole by the oil receiving plate. Since the oil is supplied into the gear device, the lubricating oil is efficiently lubricated and the lubricating oil is also efficiently stored in the oil reservoir groove communicating with the second lubricating oil hole. In addition, since the first lubricating oil hole is provided on the outer peripheral side around the rotation center on the inner peripheral surface of the hole holding the pinion shaft of the carrier, when the vehicle stops, the planet When the gear device is positioned below the rotation axis of the carrier with respect to the ground, the first lubricating oil hole is positioned below the pinion shaft with respect to the ground, so that the lubricating oil that falls due to gravity is received by the oil. The oil is efficiently stored in the oil reservoir groove through the first lubricating oil hole from the plate. On the other hand, even when the planetary gear device is located above the rotation axis of the carrier with respect to the ground, the first lubricating oil hole is located above the pinion shaft with respect to the ground, so that the stored lubricating oil is The lubricating oil does not flow out of the first lubricating oil hole and is reliably stored in the oil reservoir groove.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a cross-sectional view illustrating in detail the configuration of a vehicular automatic transmission 10 (hereinafter referred to as a transmission 10) to which the present invention is applied. The transmission 10 is disposed between an engine (not shown) and drive wheels, and shifts the rotation transmitted from the engine and transmits the rotation to the drive wheels. Since the transmission 10 of FIG. 1 is configured symmetrically with respect to the axis C, the lower side thereof is omitted.

  The transmission 10 includes an input shaft 14 to which an output of an engine (not shown) is transmitted via a torque converter in a housing case 12 (hereinafter referred to as a case 12) that is a non-rotating member attached to the vehicle, and an input thereof. And a planetary gear device 16 disposed concentrically with the axis C of the shaft 14. The planetary gear device 16 is a double pinion type planetary gear device, and meshes with the ring gear 42 of the planetary gear device 16 by another pinion gear (not shown).

  The input shaft 14 is rotatably supported by a plurality of bearings such as a bearing 18 and includes a flange portion 14a extending radially outward. The thrust bearings 20 and 22 are in contact with both sides of the flange portion 14a in the axial direction, and receive a thrust force from the flange portion 14a. One end side of the carrier 24 of the planetary gear device 16 is connected to the outer peripheral edge of the flange portion 14a by welding, and the rotation from the input shaft 14 is transmitted to the carrier 24 without being shifted.

  The inner peripheral surface of the sun gear 26 of the planetary gear device 16 is spline fitted to the outer peripheral surface of the cylindrical member 28 that functions as a non-rotating member by being connected to the case 12, so that the sun gear 26 is similarly non-rotating member. Function as.

  As described above, the carrier 24 of the planetary gear unit 16 is rotationally driven integrally with the input shaft 14. Further, one end side in the axial direction of the carrier 24 is connected to the flange portion 14a of the input shaft 14, and the other end side of the carrier 24 extends radially outward from the outer peripheral edge of the carrier 24 and extends from the outer peripheral edge to the shaft. A hub portion 24a having a cylindrical portion parallel to the center is provided.

  A plurality of friction plates 30 are spline fitted to the outer peripheral surface of the hub portion 24a so as to be movable in the axial direction. Further, the other plurality of friction plates 32 interposed between the friction plates 30 are spline-fitted to the small drum 34 so as to be movable in the axial direction. The plurality of friction plates 30 and 32 constitute a friction engagement element 36.

  The small drum 34 is a member having a double cylindrical opening at one end and a bottom wall at the other end. In order to press the friction engagement element 36 in a circumferential groove formed by the double cylinder. The piston 38 is arranged. When the piston 38 is moved by hydraulic pressure and presses the friction engagement element 36, the carrier 24 of the planetary gear device 16 and the small drum 34 are engaged, and rotation is transmitted to the small drum 34. Further, the large drum 40 is disposed so as to cover the small drum 34, and the small drum 34 and the large drum 40 are spline-fitted to each other, so that the rotation is transmitted to the large drum 40 in the same manner. The large drum 40 is also a member that has a double cylindrical opening at one end and a bottom wall at the other end.

  The ring gear 42 of the planetary gear device 16 is meshed with the sun gear 26 via a pinion gear 44. A plurality of friction plates 30 are spline fitted to the outer peripheral surface of the ring gear 42 so as to be movable in the axial direction. The other friction plate 32 interposed between the friction plates 30 is spline-fitted to the inner peripheral surface of the large drum 40 so as to be movable in the axial direction. These friction plates 30 and 32 constitute a friction engagement element 46. A piston 48 for pressing the friction engagement element 46 is accommodated in a circumferential groove formed by the double cylinder of the large drum 40. When the friction engagement element 46 is engaged by the piston 48, the rotation of the ring gear 42 is transmitted to the large drum 40. The ring gear 42 is also connected to the rotation transmission member 50, and the rotation of the rotation transmission member 50 and the large drum 40 is transmitted to other rotation elements (not shown) of the transmission 10.

  FIG. 2 is an enlarged cross-sectional view of the planetary gear device 16 of FIG. The planetary gear device 16 corresponds to the planetary gear device of the present invention. The pinion shaft 52 of the planetary gear device 16 is press-fitted into a pair of fixing holes 54 provided at both ends of the carrier 24 around the axis C of FIG. A pinion gear 44 is rotatably fitted to the outer peripheral surface of the pinion shaft 54 via a needle bearing 56. Although the carrier 24 is separated on both sides of the pinion gear in FIG. 2, the carriers 24 on both sides are integrally connected at other portions in the circumferential direction of the carrier 24 where the pinion gear 44 is not disposed. The needle bearing 56 corresponds to the bearing of the present invention.

  Lubricating oil is provided on the outer peripheral side of the fixing hole 54 holding the pinion shaft 44 of the carrier 24 connected to the hub portion 24a side as viewed from the axis C which is the center of rotation of the carrier 24. In order to supply the bearing 56, a first through hole 57 having a semicircular cross section penetrating in the thickness direction of the carrier 24 is formed by the carrier 24 and the pinion shaft 52. The first through hole 57 corresponds to the first lubricating oil hole of the present invention.

  Two washers are interposed between the carrier 24 and both sides of the pinion gear 44 in the rotational axis direction. Here, washers 58 and 60 are fitted to the pinion shaft 52 between the carrier 24 and the pinion gear 44 on the side to which the flange portion 14 a of the input shaft 14 is connected. In the washers 58 and 60, for example, the washer 58 is made of a copper alloy, the washer 60 is made of a steel material, and the two washers 58 and 60 are made of different metal materials.

  On the other hand, washers 62 and 64 are fitted to the pinion shaft 52 between the carrier 24 on the side to which the hub portion 24 a is connected and the pinion gear 44. In the washers 62 and 64, for example, the washer 62 is made of a copper alloy, and the washer 64 is made of a steel material, which are made of different metal materials.

  FIG. 3 is an enlarged view for explaining the structure of the washers 62 and 64, and FIG. 4 is an arrow view of the washer 62 of FIG. As shown in FIG. 3, an annular notch 68 is provided on one end side of the inner peripheral surface of the washer 62. The notch 68 forms a notch surface 68a that is recessed in the axial direction shown in FIG. As shown in FIG. 4, the washer 62 is provided with four through-grooves 70 having a substantially semicircular cross section at equal angular intervals on the circumference of the shaft hole 69 into which the pinion shaft 52 is fitted. Note that the pinion shaft 52 is fitted into the shaft hole 69 so that the lubricating oil supplied from the first through hole 57 of the carrier 24 passes through the washer 62 in the thickness direction so as to be supplied to the needle bearing 56 in FIG. The second through hole 72 shown is formed. The washer 64 is different from the washer 62 only in the material of the washer 62, and the shape is the same. Therefore, the washer 64 is similarly provided with a notch 68, a shaft hole 69, and a through groove 70. The second through hole 72 corresponds to the second lubricating oil hole of the present invention.

  Further, when assembling, as shown in FIG. 3, the washer 62 and 64 are assembled so that the surfaces on which the notches 68 are provided overlap each other. As a result, an annular oil reservoir groove 74 is formed at the contact portion of the washers 62 and 64.

  Returning to FIG. 2, the carrier 24 on the side where the hub portion 24 a is provided is connected to the annular oil reservoir groove 74 through the first through hole 57 on the surface opposite to the pinion gear 44 side, and on the inner peripheral side. An annular oil receiving plate 78 is provided that forms an annular oil receiving groove 76 that opens toward the front. The oil receiving plate 78 is integrally fixed to the carrier 24 by spot welding, for example.

  In the transmission 10 configured as described above, when the input shaft 14 is driven to rotate by an engine (not shown), frictional heat is generated in the planetary gear device 16 by the high-speed rotation of the pinion gear 44. With respect to this frictional heat, the lubricating oil passes through the lubricating oil supply hole 82 formed in the radial direction from the lubricating oil supply hole 80 formed in the shaft center of the input shaft 14 shown in FIG. Supplied in. This lubricating oil is released radially outward by centrifugal force, lubricates the bearing 18 and the thrust bearing 20, and is passed by the oil receiving plate 78 via the gap between the sun gear 26 of the planetary gear device 16 and the meshing portion 84 of the pinion gear 44. It is efficiently supplied into the planetary gear unit 16. The lubricating oil supplied by the oil receiving plate 78 effectively lubricates the needle bearing 56 via the first through hole 57 and the second through hole 72 shown in FIG. 2 is stored in an oil reservoir groove 74 on the side approaching the axis C in FIG.

  Further, when the vehicle stops, for example, when the planetary gear device 16 is positioned above the axis C with respect to the ground as shown in FIG. 2, the first through hole 57 of the pinion shaft 52 is based on the ground. Since it is always above the axis D, the outflow of the lubricating oil from the first through hole 57 is prevented, and the lubricating oil can be stored for a long time.

  On the other hand, for example, when the vehicle stops and the planetary gear unit 16 is positioned below the axis C with respect to the ground as shown in FIG. 5, the oil receiving plate 78 receives the lubricating oil that falls due to gravity. Due to the shape, a large amount of lubricating oil passes through the first through hole 57 and is stored in the oil reservoir 74, and the lubricating oil can be stored for a long time. As described above, when the vehicle stops, the lubricating oil can be reliably stored in the oil reservoir groove 74 regardless of the position of the planetary gear unit 16 and can be stored for a long time. . The lubricating oil stored in the oil reservoir groove 74 is supplied into the planetary gear device 16 when the planetary gear device 16 is rotated by input from the drive wheels of the vehicle when the vehicle is towed.

  As described above, according to the present embodiment, the annular circumferential oil reservoir groove 74 is provided on the inner peripheral surfaces of the washers 62 and 64, so that the vehicle is driven when the vehicle is towed. Since the planetary gear unit 16 of the transmission 10 is rotated from the rotation and the lubricating oil is required as it rotates, the lubricating oil is appropriately supplied into the planetary gear unit 16 from the annular oil retaining groove 74. Seizure of the device 16 is prevented.

  Further, according to the present embodiment, the oil reservoir groove 74 is configured by the two washers 62 and 64, so that the oil reservoir groove 74 can be easily processed and the productivity is improved. Further, the pinion gear 44 and one washer 62, the one washer 62 and the other washer 64, the other washer 64 and the carrier 24 are in contact with each other and rotate relative to each other, but only one washer is provided. In comparison, since the relative rotational speed between the members is reduced, wear and heat generation between the members are suppressed, and the durability of the planetary gear device 16 is improved.

  Further, according to this embodiment, the two washers (58, 60 and 62, 64) are made of different metal materials, so that the washers 60, 64 on the side in contact with the pinion gear 44 are, for example, steel materials. Therefore, the durability of the planetary gear unit 16 is further improved.

  Further, according to the present embodiment, the lubricating oil blown by the centrifugal force is supplied by the oil receiving plate 78 into the planetary gear device 16 via the first through hole 57 and the second through hole 72. Lubricating oil is efficiently supplied, and the lubricating oil is also efficiently stored in the oil reservoir groove 74 communicating with the second through hole 72. Further, since the first through hole 57 is provided on the outer peripheral side around the rotation center of the carrier 24 on the inner peripheral surface of the fixing hole 54 holding the pinion shaft 44 of the carrier 24, the vehicle stops. When the planetary gear device 16 is positioned below the rotational axis C of the carrier 24 with respect to the ground, the first through hole 57 is positioned below the axis D of the pinion shaft 52 with respect to the ground. The lubricating oil falling due to gravity is efficiently stored in the oil reservoir groove 74 from the oil receiving plate 78 through the first through hole 57. On the other hand, even when the planetary gear device 16 is located above the rotation center of the carrier 24 with respect to the ground, the first through hole 57 is located above the axis D of the pinion shaft 52 with respect to the ground. The stored lubricating oil is reliably stored in the oil storage groove 74 without flowing out of the first through hole 57.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, in the planetary gear device 16 of the present embodiment, the oil reservoir groove 74 is provided in the washers 62 and 64 on one side of the pinion gear 44, but the oil reservoir groove 74 may be provided in the washers 58 and 60 on the other side. The present invention can be implemented by providing oil reservoir grooves 74 on both sides of the pinion gear 44.

  In the planetary gear device 16 of the present embodiment, the lubricating oil is supplied from the oil receiving plate 78, but the lubricating oil is supplied from the inside of the pinion shaft 52 toward the inner peripheral surface of the pinion gear 44 as in the conventional planetary gear device. The present invention can be implemented even if the oil reservoir groove 74 is provided in the washers 62 and 64. That is, the lubricating oil is stored in the oil reservoir groove 74 in any type of supply method of the lubricating oil, so that the lubricating oil can be supplied when the vehicle is towed.

  Further, the oil reservoir groove 74 of the present embodiment is formed by superposing two washers 62 and 64, but it is not necessarily constituted by two washers, and may be constituted by one washer. In addition, the oil reservoir groove 74 can be formed with three or more washers.

  Moreover, although the washer of a present Example is comprised with the metal material from which adjacent washers differ, it can also comprise and implement with the same kind of metal material.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

It is sectional drawing explaining the structure of the automatic transmission for vehicles to which this invention was applied in detail. It is sectional drawing to which the planetary gear apparatus of FIG. 1 was expanded. It is an enlarged view explaining the structure of the washer of FIG. FIG. 4 is an arrow view of the washer of FIG. 3 as viewed from the direction of arrow A. It is sectional drawing when the planetary gear apparatus of FIG. 2 is located below the rotating shaft of a carrier.

Explanation of symbols

10: Automatic transmission for vehicle 16: Planetary gear device 24: Carrier 44: Pinion gear 52: Pinion shaft 56: Needle bearing (bearing) 57: First through hole (first lubricating oil hole) 58, 60, 62, 64 : Washer 68: Notch 72: Second through hole (second lubricating oil hole) 74: Oil reservoir groove 76: Oil receiving groove 78: Oil receiving plate

Claims (4)

A carrier of a planetary gear device, a pinion shaft held by the carrier, a pinion gear rotatably supported on the pinion shaft via a bearing, and the pinion being interposed between the pinion gear and the carrier A planetary gear device of a vehicle drive device comprising a washer fitted to a shaft,
A lubrication mechanism for a planetary gear device, characterized in that a circumferential annular oil reservoir groove is provided on an inner peripheral surface of the washer. The annular groove is composed of two washers, each provided with an annular notch on one end side of the inner peripheral surface of the washer,
2. The lubricating mechanism for a planetary gear device according to claim 1, wherein surfaces of the two washers where the notches are provided overlap each other to form the annular oil reservoir groove.   The lubricating mechanism for a planetary gear device according to claim 2, wherein the two washers are made of different metals. A first lubricating oil hole penetrating in the thickness direction for supplying lubricating oil to the bearing is provided on an outer peripheral side of the inner peripheral surface of the hole holding the pinion shaft of the carrier with the carrier as a rotation center. Provided,
The inner peripheral surface of the washer is provided with a second lubricating oil hole penetrating in the thickness direction in order to supply the lubricating oil supplied from the first lubricating oil hole of the carrier to the bearing,
An annular oil receiving groove that communicates with the annular oil reservoir groove through the first lubricating oil hole and opens to the inner peripheral side is formed on the surface opposite to the pinion gear side of the carrier. 4. The planetary gear unit lubrication mechanism according to claim 1, wherein an oil receiving plate is provided.

Images