JP4096519B2 - Planetary gear unit - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a planetary gear device used in an automatic transmission or the like, and more particularly to a structure for positioning and fixing a ring gear of a planetary gear device in an axial direction.
[0002]
[Prior art]
In general, a planetary gear device is used for an automatic transmission. For example, in a belt type continuously variable transmission (CVT), a dual planetary gear device is used as a forward / reverse switching device for switching forward / reverse. FIG. 5 is a view showing a conventional planetary gear device proposed by the present applicant. The forward / reverse switching device 100 is supported by the sun gear S, the ring gear R, the carrier CR, and the carrier CR, and meshes with each other and the outer planetary pinion P1 that meshes with the ring gear R and the inner planetary pinion P2 that meshes with the sun gear S. A dual planetary gear device 200 is provided.
[0003]
The sun gear S is splined to an input shaft 103 connected to an output portion of a torque converter (not shown), and the carrier CR is connected to a primary pulley 105 serving as an output member, and a forward clutch. The ring gear R is connected to the reverse brake B1 as will be described later.
[0004]
An annular cylinder member 109 is fixed to the input shaft 103, and a hydraulic actuator 111 for the clutch C1 is disposed on the inner peripheral surface side of the cylinder member 109. The clutch C1 is interposed between the inner peripheral surface of the outer wall of the cylinder member 109 and the side plate 217 constituting the carrier CR. On the other hand, a brake hydraulic actuator 123 is disposed in the partition wall portion of the case 106, and a part of the inner peripheral surface of the case 106 and an outer peripheral surface of the ring-shaped portion 230 having the ring gear R on the inner peripheral surface thereof. The brake B1 is interposed between them.
[0005]
The carrier CR includes two side plates 234 and 217, and both side plates are integrally connected by a pinion shaft 235 and a connecting portion (not shown) so as to sandwich the pinions P1 and P2. A hub member 239 is fixed to the inner peripheral portion of one side plate 234 (on the left side in FIG. 5). The hub member 239 is splined to the primary pulley 105, and via roller bearings 233 and 240. It is sandwiched between the disk-shaped member 232 and the sun gear S, and is positioned and supported.
[0006]
A disc-like member 232 is fixed to the inner peripheral surface of one end of the ring-like member 230 by welding at a portion indicated by A in the figure, and the inner peripheral side of the disc-like member 232 is supported by a thrust roller bearing 233 or the like. The ring gear R is positioned and supported by clamping.
[0007]
[Problems to be solved by the invention]
In the conventional planetary gear device 200 described above, in order to position and support the ring gear R, the ring-shaped member 230 having the ring gear R on the inner peripheral surface and the disk-shaped member 232 are fixed by welding. However, at the time of welding, there is a possibility that the accuracy of the tooth surface of the ring gear R provided on the inner peripheral surface of the ring-shaped member 230 may be deteriorated due to effects of welding such as contraction deformation due to heat and generation of residual stress. .
[0008]
Further, for example, when the brake B1 is engaged during reverse travel, the ring gear R is fixed to the case 106 in the radial direction because the ring gear R is fixed to the case 106 in the radial direction. For example, if there is a component error in each gear accuracy, carrier accuracy, etc., there is a possibility that the correction motion in the radial direction for absorbing these errors cannot be performed and gear noise is increased.
[0009]
For example, as shown in FIG. 6, the present applicant has devised a planetary gear device that supports the ring gear R without performing welding. The dual planetary gear device 200 ′ as the front / rear switching device 100 ′ includes a support member 255 in which a disk portion 232 ′ and a ring portion 230 ′ are integrally formed, and the ring gear R is connected to the inner peripheral surface of the ring portion 230 ′. It is supported in the axial direction by abutting against the snap rings 251 and 252 included in the ring, and fixed in the rotational direction by spline engagement between the ring gear R and the ring portion 230 ′, and in the radial direction. Thus, the ring gear R is positioned. In addition, the other part shown in FIG. 6 attaches | subjects the same code | symbol as FIG. 5, and the description is abbreviate | omitted.
[0010]
The planetary gear device 200 ′ can eliminate the influence of welding, and has a predetermined gap d1 as shown in FIG. 7 between the ring gear R and the ring portion 230 ′. The ring gear R can perform a correction motion to absorb errors such as the gear accuracy and the carrier accuracy as described above. However, since the ring gear R is sandwiched between the snap rings 251 and 252 and the gaps a and b for assembling are formed at two locations in each of the snap rings 251 and 252, There was a problem that the support accuracy with respect to the inclination was lowered. Further, as shown in FIG. 8, in order to reduce the inclination θ ′ of the ring gear R, it is necessary to increase the width W ′ of the ring gear R. However, increasing the width W ′ reduces the weight of the ring gear R. There has been a problem that the cost for the spline processing of the outer peripheral surface of the ring gear R increases.
[0011]
Accordingly, the present invention is a planetary gear that solves the above-described problems by engaging the ring gear with the collar portion in a non-rotatable manner and positioning the ring gear in the axial direction by a contact portion of the disk portion and a stopper member disposed at the collar portion. The object is to provide an apparatus.
[0012]
[Means for Solving the Problems]
The present invention according to claim 1 (see, for example, FIG. 1) is a planetary gear device (2) having a ring gear (R), a sun gear (S), and a carrier (CR) disposed on a predetermined shaft (eg, 3).
A support member (55) rotatably supported on the predetermined shaft (for example, 3) and having a disk portion (32) extending in the radial direction and a flange portion (30) extending in the axial direction at the tip of the disk portion (32). )When,
A stopper member (51) detachably disposed on the flange (30);
A protrusion (32a) formed in the disk portion (32) and protruding in the axial direction,
In the ring gear (R), an annular flange portion (53) having a small width with respect to the tooth width of the gear (R) is formed to protrude on the outer peripheral surface, and the flange portion (53) is formed on the outer peripheral surface of the flange portion (53). 30) The spline (53a) that engages with the spline (30b) on the inner peripheral surface of the ring gear ( 30) is non-rotatably engaged and forms the tooth width of the ring gear (R). One side surface of both side surfaces is brought into contact with the projection portion (32a), and the side surface of the flange portion (53) opposite to the projection portion (32a) in the axial direction is the gear (R) in the axial direction. By being in contact with the stopper member (51) disposed within the tooth width, the protrusion (32a) of the disk portion (32) and the stopper member (51) are positioned in the axial direction. Arranged ,
There is a space between the disk portion (32) and the flange portion (53) in the axial direction and between the outer peripheral surface of the ring gear (R) and the flange portion (30) in the radial direction.
The planetary gear device (2) is characterized in that.
[0013]
The invention according to claim 2 (e.g. see FIG. 1), the stopper member (51) is Ru snap ring der,
It exists in the planetary gear apparatus (2) of Claim 1.
[0016]
According to a third aspect of the present invention (see, for example, FIG. 1), the outer peripheral surface of the flange portion (30) has a spline (30a) with which the inner friction plate (31) of the friction engagement means (B1) is engaged. ,
It exists in the planetary gear apparatus (2) of Claim 1 or 2 .
[0017]
According to a fourth aspect of the present invention (see, for example, FIG. 1), the friction engagement means (B1) includes a brake.
It exists in the planetary gear apparatus (2) of Claim 3.
[0018]
In the present invention according to claim 5 (see, for example, FIGS. 1 and 2), the flange portion (53) has a predetermined gap (d2) between the flange portion (30) and the flange portion (30).
It exists in the planetary gear apparatus (2) in any one of Claim 1 thru | or 4.
[0019]
In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.
[0020]
【The invention's effect】
According to the first aspect of the present invention, the ring gear is engaged with the collar portion in a non-rotatable manner and is positioned in the axial direction by the protrusion of the disk portion and the stopper member, so that the ring gear is not welded. Can be arranged, the influence on the accuracy of the tooth surface of the ring gear by welding can be eliminated, and the gear accuracy of the ring gear can be improved. Furthermore, by disposing the stopper member only on one side, for example, only one gap is required for assembling the stopper member, so that the inclination of the ring gear can be reduced, and accordingly the gear accuracy is further improved. Thus, gear noise can be reduced in combination with eliminating the influence of the welding.
The ring gear has an annular flange portion that is smaller than the gear width of the gear and protrudes from the outer peripheral surface, and has a spline that engages with the spline on the inner peripheral surface of the flange portion on the outer peripheral surface of the flange portion. In particular, there is a space between the disk portion and the flange portion in the axial direction and between the outer peripheral surface of the ring gear and the flange portion in the radial direction. The spline is formed only on the outer peripheral surface of the flange portion having a small width, and the spline processing can be performed by, for example, press punching, and accordingly, the manufacturing cost can be reduced. it can.
Further, the ring gear is positioned in the axial direction by contacting the flange side surface with a stopper member disposed within the gear width of the gear in the axial direction and contacting the side surface of the gear with the projection. Therefore, the width for supporting the ring gear can be obtained without increasing the width on the outer peripheral side of the ring gear, and the weight can be reduced accordingly. Further, since the abutting portion of the disk portion is a protruding portion protruding in the axial direction, a protruding protruding portion can be formed by, for example, pressing, and the cost can be reduced.
[0021]
According to the present invention according to claim 2, scan stopper member, since it is a snap ring, can be assembled relatively easily with respect to the flange portion, and can be cost because it is relatively inexpensive .
[0024]
According to the third aspect of the present invention, since the spline is engaged with the inner friction plate of the friction engagement means on the outer peripheral surface of the flange portion, the rotation of the ring gear via the flange portion is caused by the friction engagement means. Can be controlled by.
[0025]
According to the fourth aspect of the present invention, since the friction engagement means is composed of a brake, for example, when the brake is engaged during reverse travel, the inner friction plate is fixed and the collar portion cannot be moved in the radial direction. Since the predetermined gap is provided between the ring gear and the collar portion, for example, the ring gear can perform a correction motion in the radial direction even when the vehicle is moving backward, thereby reducing gear noise.
[0026]
According to the present invention of claim 5, since the flange portion has a predetermined gap between the flange portion, even when there is a component error in the accuracy of each gear and the carrier accuracy, the ring gear is In order to absorb these errors, corrective motion in the radial direction can be performed, thereby reducing gear noise.
[0027]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view showing a forward / reverse switching device incorporated in a belt type continuously variable transmission (CVT). The forward / backward switching device 1 is supported by a sun gear S, a ring gear R, a carrier CR, and the carrier CR. And a dual planetary gear device 2 comprising a plurality of sets of an outer planetary pinion P1 meshing with the ring gear R and an inner planetary pinion P2 meshing with the sun gear S.
[0028]
The sun gear S is spline-coupled to an input shaft 3 connected to an output portion of a torque converter (not shown), and the carrier CR is connected to a primary pulley 5 serving as an output member and a forward clutch. The ring gear R (which will be described in detail later) is connected to the reverse brake B1. The forward / reverse switching device 1 is housed in a case 6 together with other devices such as a belt-type continuously variable transmission, and 7 is an oil pump.
[0029]
An annular cylinder member 9 is fixed to the input shaft 3, and a piston member 10 is fitted into the cylinder member 9 in the form of an oil and constitutes a clutch hydraulic actuator 11. In the figure, reference numeral 12 denotes a return spring that is retained by the retainer 13 by the cylinder member 9, and reference numeral 15 denotes a check ball for discharging centrifugal hydraulic pressure. A clutch plate 16 of the clutch C1 is spline-engaged on the inner peripheral surface of the outer wall of the cylinder member 9 and is supported by a snap ring 18 and is a hub portion formed on a side plate 17 constituting the carrier CR. A clutch disk 19 is splined to 17a.
[0030]
On the other hand, the partition wall 6a that supports the bearing 20 for supporting the primary pulley 5 of the case 6 is formed with an annular concave groove that constitutes a cylinder 21 on one side. The brake hydraulic actuator 23 is configured in a honeycomb shape. In the figure, reference numeral 25 denotes a return spring supported by the retainer 26 so as not to be pulled out. A spline 6 b is formed on a part of the inner peripheral surface of the case 6, and the brake plate 27 of the brake B <b> 1 is secured by a snap ring 29 and engaged with the spline. A brake disk (inner friction plate) 31 is engaged with a spline 30 a formed on the outer peripheral surface of the ring portion (saddle portion) 30. The support member 55 is formed with a disk part 32 extending in the radial direction and the ring part 30 extending in the axial direction at the tip thereof, and the inner peripheral side of the disk part 32 is sandwiched by a thrust roller bearing 33 or the like, The support member 55 is positioned and supported.
[0031]
The carrier CR includes two side plates 34 and 17, and both side plates are integrally connected by pinion shafts 35 and 36 and a connecting portion 37 so as to sandwich the pinions P1 and P2. A hub member 39 is fixed to the inner peripheral portion of the side plate 34 on one side (left side in FIG. 1). The hub member 39 is spline-coupled to the primary pulley 5, and via roller bearings 33 and 40. It is sandwiched between the disk-shaped member 32 and the sun gear S, and is positioned and supported. As described above, the other side plate (right side in FIG. 1) 17 has the hub portion 17a having splines on the outer peripheral surface, and the lubricating oil introduction plate 41 is fixed to the inner peripheral side by a rivet 44. Yes. The introduction plate 41 extends along the outer side surface (the right side surface in FIG. 1) of the side plate 17 until it has a predetermined distance from the cylinder member 9, and is formed in an uneven shape in the circumferential direction. A lubricating oil introduction groove 42 is formed between the side plate 17 and the lubricating oil supplied and scattered from the input shaft 3 side to oil holes 35a and 36a formed in the axial direction of the planetary shafts 35 and 36. .
[0032]
The input shaft 3 is formed with a lubricating oil supply hole 3a in the axial direction, and a large number of lateral holes 3b and 3c are formed from the supply hole 3a toward the outer peripheral surface of the shaft. The lubricating oil derived from these lateral holes passes through the hub member 39 and the hole 9a formed in the cylinder member 9, etc., and the bearings 33, 40, 43 and the tooth surfaces of the planetary gear device, the clutch C1 and the brake B1, and It is supplied to the lubricating oil introduction groove 42 and the like.
[0033]
An outer planetary pinion P1 and an inner planetary pinion P2 are rotatably supported on the pinion shafts 35 and 36 supported on the carrier side plates 33 and 17 via needle bearings 45 and 46, respectively. Lubricating oil guided to the oil holes 35a, 36a of each pinion shaft through the introduction groove 42 is supplied to the needle bearings 45, 46 and the meshing tooth surfaces of the pinion through the respective lateral holes (not shown). Further, a pinion thrust washer 50 is disposed between the inner and outer planetary pinions P1, P2 and the carrier side plates 33, 17.
[0034]
The ring gear R, which is an essential part of the present invention, is detachably disposed on the projecting portion (abutting portion) 32 a formed on the disk-shaped member 32 and the inner peripheral surface of the ring-shaped member 30. And the snap ring 51. The ring gear R is restricted from moving in the axial direction by one side surface of the ring gear R, which is a wide portion on the outer periphery of the ring gear R, being in contact with the protrusion 32a. An annular flange portion 53 having a small width relative to the width is formed to project, and its side surface abuts against the snap ring 51 so that the movement in the other axial direction is restricted, and is positioned and supported. . The outer peripheral surface 53a of the flange portion 53 of the ring gear R is splined, and the spline 30b formed on the inner peripheral surface of the ring portion 30 is spline-engaged with a predetermined gap d2, and the ring It engages with the portion 30 in a non-rotatable manner and is positioned and supported with respect to the radial direction.
[0035]
Next, positioning and support of the ring gear R will be described in detail with reference to the drawings. FIG. 2 is a schematic explanatory view showing a gap b between the ring gear R and the snap ring 51, and FIG. 3 is a schematic explanatory view showing positioning and support of the ring gear R. As described above, since the ring gear R has its side surface in contact with the protruding portion 32a of the disk portion 32, the snap ring 51 is disposed in contact with one side opposite to the disk portion 32. Can be positioned and supported. That is, the gap necessary for assembling the snap ring 51 to the ring portion 30 can be made only at the gap b shown in FIG. That is, for example, when two ring gaps a and b are generated by supporting the ring gear R with two snap rings (see FIG. 7), one gap ring b is obtained by using one snap ring. Therefore, it is possible to improve the support accuracy with respect to the inclination of the ring gear R, thereby improving the gear accuracy and reducing gear noise.
[0036]
Further, for example, when the brake B1 is engaged during reverse travel, the brake disc 31 is fixed, whereby the ring portion 30 is fixed to the case 106 via the brake B1, that is, the ring portion 30 is in the radial direction. It becomes impossible to move. However, since there is a predetermined gap d2 between the outer peripheral surface 53a of the flange portion 53 of the ring gear R and the spline 30b of the ring portion 30, for example, accuracy of each gear (ring gear, sun gear, carrier, etc.) and carrier accuracy Even when there is a component error in the above and the case of reverse travel, the ring gear R can perform a correction motion in the radial direction in order to absorb these errors, thereby reducing gear noise.
[0037]
Further, as shown in FIG. 3, the ring gear R is annular, so that, for example, when the ring gear R is inclined, one end side (for example, the upper side in FIG. 3) of the ring gear R is supported by the snap ring 51. The other end side (for example, the lower side in FIG. 3) is supported by the disk portion 32 (projection portion 32a). That is, since an inclination with respect to the gap b occurs in a state where both ends are supported, the inclination can be reduced and the gear accuracy is improved.
[0038]
Needless to say, it is possible to reduce the cost by arranging one snap ring rather than arranging two snap rings. Further, the projecting portion 32a of the disc portion 32 can be formed in a convex shape by, for example, pressing, and can be brought into contact with the side surface of the ring gear R without providing another member for contact, for example. Because it can, cost can be reduced.
[0039]
Next, processing of the flange portion 53 of the ring gear R will be described with reference to the drawings. FIG. 4 is a schematic explanatory view showing the flange portion 53 of the ring gear R. As shown in FIG. As described above, since the ring gear R is positioned and supported by the side surface and the side surface of the flange portion 53, for example, the width W to be supported without increasing the width of the outer peripheral surface of the ring gear R (see FIG. 8). The outer peripheral portion of the ring gear R indicated by the broken line B in FIG. 4 is unnecessary. That is, by forming the flange portion 53, the outer peripheral portion of the ring gear R indicated by the broken line B can be eliminated, and the weight can be reduced. Further, since the supporting width W can be obtained without increasing the width of the outer peripheral surface of the ring gear R, the axial direction of the ring gear R can be shortened, and the planetary gear device can be made compact. .
[0040]
Further, the spline is formed on the outer peripheral surface 53a of the flange portion 53 as described above. For example, the spline is not formed on the entire width of the ring gear R, which is a portion indicated by the broken line B, but the outer peripheral surface of the flange portion. Since the spline is formed only on 53a, the spline processing can be performed by, for example, press punching processing, and accordingly, the manufacturing cost can be reduced.
[0041]
Further, as described above, one end side of the ring gear R is supported by the snap ring 51 and the other end side is supported by the protrusion 32a (see FIG. 3), thereby forming the flange portion 53, which is indicated by the broken line B. Although the outer peripheral portion of the ring gear R is eliminated (see FIG. 4), the weight can be reduced, but the above-described substantially both-end support state is enabled.
[0042]
As described above, the planetary gear device 2 according to the present invention makes it possible to arrange the ring gear R without welding, so that the influence on the accuracy of the tooth surface of the ring gear R due to welding can be eliminated, and the ring gear R The gear accuracy can be improved. Further, by disposing the snap ring 51 only on one side, the gap necessary for assembling the snap ring is made only at one place as described above, so that the inclination of the ring gear R can be reduced. Gear noise can be reduced in combination with further improving the gear accuracy and eliminating the influence of the welding.
[0043]
In the above embodiment, the ring gear R is positioned and supported with respect to the one axial direction, and a snap ring that can be assembled relatively easily and is inexpensive is provided. Not limited to this, any ring gear R may be used as long as the ring gear R is positioned and supported in one axial direction with respect to the ring portion 30. Further, the ring gear R is positioned and supported with respect to the other axial direction by forming a convex protrusion 32a on the disk portion 32 and contacting it, but it does not have to be formed in a convex shape, for example, An abutting member may be newly provided between the ring gear R and the disk portion 32. For example, the ring gear R may be extended to the side surface. Any one can be used as long as it can be positioned and supported in the other axial direction.
[0044]
Moreover, although the said embodiment demonstrated the dual planetary gear apparatus used as a forward / reverse switching device, it is not restricted to this, The simple planetary gear apparatus used for a multistage automatic transmission, a dual planetary gear apparatus, and the planetary gear which combined the several planetary gear Of course, the present invention can be applied to a device, and can also be applied to a planetary gear device other than an automatic transmission.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a forward / reverse switching device incorporated in a belt type continuously variable transmission.
FIG. 2 is a schematic explanatory view showing a gap between a ring gear and a snap ring.
FIG. 3 is a schematic explanatory view showing positioning and support of a ring gear.
FIG. 4 is a schematic explanatory view showing a flange portion of a ring gear.
FIG. 5 is a view showing a conventional planetary gear device proposed by the present applicant.
FIG. 6 is a view showing a conventional planetary gear device devised by the present applicant.
FIG. 7 is a schematic explanatory view showing a gap between a conventional ring gear and a snap ring.
FIG. 8 is a schematic explanatory view showing positioning and support of a conventional ring gear.
[Explanation of symbols]
2 Planetary gear device 30 heel part (ring part)
30a Spline 30b Spline 31 Internal friction plate (brake disc)
32 Disc part 32a Contact part (protrusion part)
51 Stopper member (snap ring)
53 Flange 53a Spline 55 Support member R Ring gear S Sun gear CR Carrier B1 Friction engagement means (brake)
d2 Predetermined gap

Claims (5)

In a planetary gear device having a ring gear, a sun gear and a carrier arranged on a predetermined axis,
A support member rotatably supported on the predetermined axis and having a disk portion extending in the radial direction and a flange portion extending in the axial direction at the tip of the disk portion;
A stopper member detachably disposed on the collar,
A protrusion formed on the disk portion and protruding in the axial direction,
In the ring gear, an annular flange portion having a small width with respect to the gear width of the gear is formed to protrude on the outer peripheral surface, and the flange portion outer peripheral surface has a spline that engages with a spline on the inner peripheral surface of the flange portion. Thus, it engages with the collar portion in a non-rotatable manner, and one side surface of both side surfaces forming the tooth width of the ring gear is brought into contact with the projection portion, and is opposite to the projection portion in the axial direction. The flange portion side surface of the disc portion is in contact with the stopper member disposed within the gear width of the gear in the axial direction, so that the flange portion is positioned in the axial direction by the protrusion portion of the disk portion and the stopper member. It is,
Between the disk portion and the flange portion in the axial direction and having a space between the outer peripheral surface of the ring gear and the flange portion in the radial direction,
A planetary gear device characterized by that. The stopper member is a snap ring.
The planetary gear device according to claim 1. The outer peripheral surface of the flange has a spline with which the inner friction plate of the friction engagement means engages.
The planetary gear device according to claim 1 or 2. The friction engagement means comprises a brake;
The planetary gear device according to claim 3. The flange portion has a predetermined gap between the flange portion and the flange portion.
The planetary gear device according to any one of claims 1 to 4.

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