JP5649173B2 - Planetary carrier - Google Patents

Description

  The present invention relates to a planetary carrier of a planetary gear mechanism mounted on a vehicle such as an automobile, and more particularly to a planetary carrier having an inner spline and an outer spline.

  A planetary gear mechanism is used for a forward / reverse switching mechanism of a continuously variable transmission (CVT) such as an automobile. Some planetary carriers of planetary gear mechanisms have an inner spline and an outer spline for spline fitting a clutch disc and a brake disc. In this type of planetary carrier, only the inner spline is formed from one end surface of the planetary carrier, and the outer spline is not formed from one end surface of the planetary carrier (see, for example, Patent Document 1).

  5 and 6 are diagrams showing an example of this type of planetary carrier. The planetary carrier 200 shown in the figure is formed on a boss portion 210, a disk portion 220 formed radially outward from one axial end side of the boss portion 210, and an axially outer side portion of the disk portion 220. A substantially cylindrical tubular portion 230. An inner spline 231 and an outer spline 232 are formed on the inner side and the outer side of the cylindrical portion 230, respectively. The circumferential pitches (phases) of the spline teeth of the inner spline 231 and the outer spline 232 coincide with each other. Further, as described above, the inner spline 231 is formed from one end surface 236 of the planetary carrier 200 (cylindrical portion 230), whereas the outer spline 232 is one end surface of the planetary carrier 200 (cylindrical portion 230). 236 is not formed. That is, the outer peripheral portion of the cylindrical portion 230 is a cylindrical surface 233 within a predetermined range in the axial direction from the one end surface 236.

  The cylindrical portion 230 of the planetary carrier 200 is formed with a planetary gear installation space 238 and a pin hole 234 through which the planetary gear shaft pin is inserted. In order to form the pin hole 234, a part of the inner spline 231 is missing, and a recess 235 that is recessed radially outward is formed at a location corresponding to the pin hole 234 of the missing tooth portion 2311. . The recess 235 is provided for processing the pin hole 234 and is formed in the vicinity of the extension line of the pin hole 234. In the portion where the concave portion 235 is formed, the thickness T in the radial direction of the cylindrical portion 230 becomes thin.

JP 2009-142935 A

  By the way, when the planetary carrier is manufactured by aluminum die casting, it is necessary to secure a seating surface 237 (see FIG. 6) for the extrusion pin having a predetermined size (diameter) on the one end surface 236 of the cylindrical portion 230 at the time of casting. . However, in the conventional planetary carrier, since the space of the one end surface 236 of the cylindrical part 230 is small, it may be difficult to secure the seating surface on the one end surface 236. Of course, by increasing the diameter of the outer spline 232 or decreasing the diameter of the inner spline 231, it is possible to increase the space of the one end surface 236 of the cylindrical portion 230 and secure the seating surface. However, if it does so, there is a concern that the size of the planetary carrier 200 will increase and the size and weight of the entire planetary gear mechanism will increase significantly.

  The present invention was devised in view of such a problem, and it is possible to easily secure a seating surface for an extrusion pin on one end surface of the planetary carrier without changing the diameter size of the inner spline and the outer spline of the planetary carrier. The purpose is to provide a career.

  As means for solving the above-described problems, the planetary carrier of the present invention is configured as follows.

  That is, the planetary carrier of the present invention is provided with a substantially cylindrical tubular portion in which an inner spline and an outer spline are formed, and the inner spline is assumed to be formed from one end surface of the tubular portion, From the outer spline to the one end surface of the cylindrical portion, a convex line continuous to the spline teeth of the outer spline is formed, and the thickness of the end surface is increased by the convex line.

  According to the planetary carrier having such a configuration, since the ridges are formed from the outer spline to one end surface of the cylindrical portion, the diameter of the inner spline and the outer spline can be changed without changing the diameter size. The space of the one end surface of a shape part can be made wider than before. As a result, it becomes easier to secure the seating surface for the push pin than the conventional planetary carrier. Furthermore, the strength, rigidity, etc. of the planetary carrier are improved.

  It is desirable that the tooth width and the tooth root diameter of the ridges are reduced toward the one end surface side by a die cutting gradient.

  Comparing the backlash when the disc such as the brake plate is fitted to the outer spline with the spline and the backlash when the disc such as the brake plate is fitted to the ridge is compared, the latter is larger. Further, since the disc such as the brake plate is assembled to the outer spline from the one end surface side of the cylindrical portion through the ridge, this ridge serves as a guide to the outer spline. Assemblability is improved.

  According to the planetary carrier of the present invention, a ridge that is continuous with the spline teeth of the outer spline is formed from the outer spline to one end surface of the cylindrical portion, and the thickness of the end surface is increased by the ridge. Thus, the space on the one end face of the cylindrical portion can be made wider than before without changing the diameter size of the inner spline and the outer spline. As a result, it becomes easier to secure the seating surface for the push pin than the conventional planetary carrier. Furthermore, the strength, rigidity, etc. of the planetary carrier are improved.

It is a skeleton figure which shows the power train of the vehicle carrying the planetary gear mechanism which has the planetary carrier which concerns on embodiment of this invention. It is the figure which looked at the planetary carrier which concerns on embodiment of this invention from one side of the axial direction. It is AA sectional drawing of FIG. It is the B section enlarged view of FIG. It is sectional drawing which cut | disconnected and represented the planetary carrier which concerns on a prior art example by the plane containing an axis line. It is C arrow line view of FIG.

  Hereinafter, a planetary carrier according to an embodiment of the present invention will be described with reference to the drawings. In the present embodiment, a planetary carrier included in a planetary gear mechanism of a forward / reverse switching device mounted on a vehicle together with a belt type continuously variable transmission will be described as an example.

  FIG. 1 shows a power train of a vehicle equipped with a belt type continuously variable transmission. The vehicle shown in FIG. 1 is an FF (front engine / front drive) type vehicle, and includes an engine 1, a torque converter 2, a forward / reverse switching device 3, a belt-type continuously variable transmission 4, a reduction gear device 5, a differential gear. A gear device 6 and the like are mounted.

  A crankshaft 11, which is an output shaft of the engine 1, is connected to the torque converter 2, and the output of the engine 1 is transmitted from the torque converter 2 to the forward / reverse switching device 3, the belt type continuously variable transmission 4, and the reduction gear device 5. To the differential gear device 6 and distributed to the left and right drive wheels (not shown).

  The forward / reverse switching device 3 includes a planetary gear mechanism 30, a multi-plate clutch 60, and a multi-plate brake 50. Hereinafter, the clutch 60 and the brake 50 are simply referred to. The planetary gear mechanism 30 illustrated in FIG. 1 is of a single pinion type, a sun gear 31 is connected to the turbine shaft 28, and a ring gear 32 is connected to the input shaft 40 of the belt type continuously variable transmission 4. . The brake 50 is used to stop the rotation of the planetary carrier 100, and the clutch 60 is used to fasten the planetary carrier 100 and the sun gear 31 together. The planetary carrier 100 is rotatably installed on the same axis as the turbine shaft 28 and supports the planetary gear 33 so as to be capable of rotating.

  When the clutch 60 is released and the brake 50 is engaged, the rotation of the planetary carrier 100 is restricted, and the rotation of the turbine shaft 28 is reversed and decelerated by the sun gear 31, the planetary gear 33, and the ring gear 32 and transmitted to the input shaft 40. . On the other hand, when the brake 50 is released and the clutch 60 is engaged, the planetary carrier 100 and the sun gear 31 rotate together, and the turbine shaft 28 and the input shaft 40 are directly connected. Further, when both the clutch 60 and the brake 50 are released, the forward / reverse switching device 3 cuts off the power to form a neutral state.

  The belt-type continuously variable transmission 4 includes an input-side primary pulley 41, an output-side secondary pulley 42, and a metal belt 43 wound between the primary pulley 41 and the secondary pulley 42.

  Hereinafter, the planetary carrier 100 according to the present embodiment will be described in more detail.

  As shown in FIGS. 2 to 4, the planetary carrier 100 includes a boss portion 110, a disc portion 120 formed radially outward from one axial end side of the boss portion 110, and an outer peripheral portion of the disc portion 120. And a substantially cylindrical tubular portion 130 formed on one side in the axial direction. These parts 110 to 130 are integrally formed. For this planetary carrier 100, for example, iron, copper, carbon sintered material, aluminum die-casting, or the like can be adopted. In this embodiment, aluminum die-casting is adopted.

  An inner spline 131 and an outer spline 132 are formed on the inner side and the outer side of the cylindrical portion 130, respectively. The outer spline of the clutch plate 61 (see FIG. 1) of the clutch 60 is spline fitted to the inner spline 131. On the other hand, the inner peripheral portion of the brake plate 51 of the brake 50 is spline fitted to the outer spline 132.

As shown in FIG. 3, a ridge 133 is formed between the outer spline 132 and the one end surface 136 between the outer spline 132 and the one end surface 136 of the cylindrical portion 130. The ridge 133 is continuous with each spline tooth of the outer spline 132. The protrusion 133 is formed until it extends over the one end surface 136 of the tubular portion 130, and the thickness of the end surface is increased by the protrusion, so that the space of the one end surface 136 of the tubular portion 130 is widened. As a result, it becomes easy to secure a seating surface for an extrusion pin of a predetermined size. Furthermore, the strength, rigidity, etc. of the planetary carrier are improved.

  For example, the protrusion 133 can be formed by forming the outer spline 132 up to one end 136 of the cylindrical portion 130 and reducing the diameter of the tooth tip.

  Further, in the planetary carrier 100 according to the present embodiment, the circumferential pitch (phase) of the inner spline 131 and the protrusion 133 (outer spline 132) is different, and a plurality of locations (reference numeral 137 in FIGS. 2 and 4). In the illustrated portion, the circumferential positions of the ridge 133 and the spline teeth of the inner spline 131 coincide with each other. Thereby, if the said coincidence part is made into the seat surface 137 for an extrusion pin, it will become easy to ensure the seat surface for an extrusion pin further.

  The spline teeth of the outer spline 132 and the ridge 133 have the same shape except for the tooth height, and although not shown in detail, the tooth width 1331 and the root diameter 1332 of the ridge 133 are axially extended due to the die-cutting gradient. The one end surface 136 side is reduced. Comparing the backlash when the brake plate 51 is spline-fitted with the outer spline 132 and the backlash when the brake plate 51 is fitted with the protrusion 133, the latter is larger and the brake plate 51 Is assembled to the outer spline 132 from the one end surface 136 side of the cylindrical portion 130 through the protruding line 133, so that the protruding line 133 serves as a guide when assembled to the outer spline 132. That is, the protrusions 133 serve as a guide when assembling to the outer spline 132, so that the assembling property when the brake plate 51 is assembled to the outer spline 132 is improved.

  The cylindrical portion 130 of the planetary carrier 100 is provided with an installation space 138 for the planetary gear 33 and a pin hole 134 through which the shaft pin of the planetary gear 33 is inserted. As shown in FIG. 4, in order to form the pin hole 134, a part of the inner spline 131 is missing and a missing tooth portion 1311 is formed. Further, on the inner periphery of the cylindrical portion 130, a concave portion 135 that is recessed outward in the radial direction is formed at a location corresponding to the pin hole 134. The recess 135 is necessary when the pin hole 134 is processed, and is formed in the vicinity of the extension line of the pin hole 134.

  In the cylindrical portion 130, the thickness T in the radial direction is reduced in the portion where the concave portion 135 is formed, but the protrusion 133 extends to one end surface 136 of the cylindrical portion 130 as compared with the conventional planetary gear. As the area of the one end face 136 is increased, the thickness T is also increased. Thereby, the strength, rigidity, etc. of the planetary carrier 100 are improved.

  In the above-described embodiment, the number of the ridges 133 matches the number of all the spline teeth of the outer spline 132, but the number of the ridges 133 is set to be smaller than the number of spline teeth of the outer spline 132. May be. Of course, it is desirable that the seating surface 137 of the push pin is provided in a portion of the one end surface 136 where the protrusions 133 are formed.

  The present invention can be applied to a planetary carrier of a planetary gear mechanism mounted on a vehicle such as an automobile.

DESCRIPTION OF SYMBOLS 100 Planetary carrier 130 Cylindrical part 131 Inner spline 132 Outer spline 133 Convex strip 136 One end surface 1331 The tooth width of a convex strip 1332 The root diameter of a convex strip

Claims (1)

In a planetary carrier comprising a substantially cylindrical tubular part in which an inner spline and an outer spline are formed, wherein the inner spline is formed from one end surface of the tubular part,
A ridge that continues to the spline teeth of the outer spline is formed from the outer spline to the one end surface of the cylindrical portion, and the thickness of the one end surface is increased by the ridge. Planetary carrier.