JP4026828B2 - Connecting shell connection structure - Google Patents

Description

  The present invention belongs to a technical field of a connecting shell connecting structure in which a connecting shell is connected to a drum of an automatic transmission and rotated integrally.

  2. Description of the Related Art Conventionally, in an automatic transmission, a drum and a connecting shell are coupled and rotated together using a meshing structure. This meshing structure consists of a number of notch grooves provided in the axial direction by notching the outer periphery of the drum at equal intervals, and a notch protrusion provided by notching the circumferential end of the connecting shell. It is the structure which connects and couples.

  In this structure, since the torque in the axial direction and the rotational direction is transmitted through the contact surface between the notch groove of the drum and the notch convex portion of the connecting shell, the contact area is insufficient and there is a risk of buckling deformation or compression deformation.

Therefore, in order to solve this problem, in the connecting structure of the connecting shell in the conventional automatic transmission, the thickness of one or both of the contact portions of the drum and the connecting shell is increased in order to increase the contact area of the meshing portion. This increases the contact area and prevents buckling deformation and the like (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 8-100845

  In the above prior art, in order to transmit the torque in the axial direction and the rotational direction at all the notches of the drum, a straight surface for axial positioning is provided in the recesses of all the notches of the drum. In order to secure this straight surface, it was necessary to reduce the machining allowance for the recess at the base of the notch. However, if the machining allowance is reduced, stress concentration may occur at the base of the notch and the durability may be reduced. Therefore, it is necessary to increase the thickness of the entire coupling portion in order to ensure the strength, which hinders weight reduction.

  The present invention has been made paying attention to the above-mentioned problems, and an object of the present invention is to provide a connecting shell coupling structure capable of further improving durability without incurring a cost increase. is there.

In order to achieve the above object, according to the present invention, in the connecting shell coupling structure, the notch groove of the drum has a positioning groove that determines the axial position of the drum and a torque transmission groove that handles torque transmission in the rotational direction. In addition, the groove width of the positioning groove is wider than the width of the notch convex portion .

  Therefore, in the present invention, the member can be thinned by relaxing the stress concentration applied to the axial positioning groove by sharing the axial positioning and the rotational torque with separate parts in the coupling portion. Thus, it is possible to provide a lightweight coupling structure while improving durability.

  The best mode for carrying out the present invention will be described below based on the first embodiment.

First, the configuration will be described.
FIG. 1 is a schematic diagram illustrating the overall configuration of the first embodiment. The rotation output from the engine 1 is input to the torque converter 2 via the engine output shaft E1, and the rotation with the increased torque is input to the transmission mechanism via the input shaft Input. The torque converter 2 includes a lock-up clutch mechanism, and when the torque transmission efficiency decreases, the engine output shaft E1 and the input shaft Input are directly connected.

  The speed change mechanism unit is composed of the first planetary gear G1 and the planetary gear set GS, and outputs the rotation input from the input shaft Input from the output gear Output.

  The first planetary gear G1 is a single pinion planetary gear serving as a reduction gear having a first sun gear S1, a first ring gear R1, and a first carrier C1 that supports a first pinion P1 that meshes with both gears S1 and R1. It is.

The planetary gear set GS includes a second planetary gear G2 and a third planetary gear G3.
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier C2 that supports a second pinion P2 that meshes with both the gears S2 and R2.
The third planetary gear G3 includes a third sun gear S3 and a fourth sun gear S4, a third pinion P3 that meshes with each of the third and fourth sun gears S3 and S4, and a third axial pinion that supports the third pinion P3. A double sun gear planetary gear having a carrier C3, a center member CM connected to the third carrier C3 and disposed between the two sun gears S3 and S4, and one third ring gear R3 meshing with the third pinion P3 It is. The center member CM is coupled to the third carrier C3 at a spatial position with a plurality of third pinions P3 adjacent on the circumference of the third carrier C3.

  The input shaft Input is connected to the first ring gear R1 and inputs the rotational driving force from the engine 1 as a driving source via the torque converter 2.

  The output gear Output is connected to the second carrier C2, and transmits the output rotational driving force to the driving wheels via a final gear or the like not shown.

  The second sun gear S2 and the third sun gear S3 are integrally connected by a first connecting member M1. The second carrier C2 and the third ring gear R3 are integrally connected by a second connecting member M2.

  The low clutch L / C selectively connects and disconnects the first carrier C1 and the second ring gear R2. The 3-5 reverse clutch 3-5R / C selectively connects and disconnects the first carrier C1 and the second sun gear S2. The high clutch H / C selectively connects and disconnects the input shaft Input and the center member CM.

  The low reverse brake L & R / B selectively stops the rotation of the third carrier C3. The 2-6 brake 2-6 / B selectively stops the rotation of the fourth sun gear S4.

  Each of the clutches L / C, 3-5R / C, H / C and brakes L & R / B, 2-6 / B has 6 forward speeds, 1 reverse speeds as shown in the engagement operation table of FIG. A shift hydraulic pressure control device (not shown) that generates a fastening pressure (◯ mark) and a release pressure (no mark) at the gear stage is connected. Note that a hydraulic control type, an electronic control type, a hydraulic pressure + electronic control type, and the like are employed as the transmission hydraulic pressure control device.

  FIG. 3 is a collinear diagram showing a rotation stop state of members at each of the sixth forward speed and the reverse first speed in the automatic transmission according to the first embodiment. 1st to 6th speed and 1st reverse speed are achieved according to the fastening operation table shown in FIG.

FIG. 4 is a cross-sectional view of the overall configuration of the automatic transmission.
The first carrier C1 of the first planetary gear G1 is connected to the rotating shaft 9, and the clutch drum 3 is connected to the outer peripheral side end of the rotating shaft 9.

  The drum 10 is connected to the output gear Output, and further connected to the connecting shell 20 by meshing.

  The connecting shell 20 is connected to the third ring gear R3 of the third planetary gear G3 by welding, and the third ring gear R3 is connected to the second connecting member M2 by welding.

  The clutch drum 3 has a first spline portion 3a that is spline-fitted with the drive-side clutch plate of the low clutch L / C, and a second spline-fitted with the drive-side clutch plate of the 3-5 reverse clutch 3-5R / C. A spline portion 3b is provided.

  A first piston 4 is provided inside the clutch drum 3, and a pressing portion 4 a that presses the low clutch L / C is provided at an end of the first piston 4 on the low clutch L / C side.

  The driven clutch plate of the low clutch L / C is provided with a first clutch hub 6 by spline fitting, and the first clutch hub 6 is supported by a support member 5 extending in the radial direction.

  The support member 5 is pinched so as to be rotatable relative to the second carrier C2 and the second clutch hub 7 of the second planetary gear G2 via a thrust bearing.

  The 3-5 reverse clutch 3-5R / C is splined with the second clutch hub 7 and is pressed by the second piston 8. The second clutch hub 7 is connected to the first member M1.

FIG. 5 is a detailed view of the drum 10.
A first groove 11 for positioning the drum 10 in the axial direction and a second groove 12 for transmitting the rotational torque of the drum 10 to the connecting shell 20 are provided at the left end of the drum 10 in the drawing.

  The concave portion of the first groove 11 is provided with a straight surface 11a for positioning, and the concave portion of the first groove 11 is provided with a machining allowance 11c necessary for processing the straight surface 11a, thereby forming R. is doing. Details of R will be described later.

  A second groove side surface 12 a that is a surface for transmitting torque is provided on the groove side surface of the second groove 12, and R is provided on the second groove concave portion 12 b that is a concave portion of the second groove 12.

  The first groove side surface 11 b which is the side surface of the first groove 11 does not participate in torque transmission, and the number of grooves of the first groove 11 is smaller than the number of grooves of the second groove 12.

  In order to evenly share the axial force, the grooves at the end of the drum 10 in the axial direction are provided with one first groove 11 and a plurality of second grooves 12 at equal intervals. Has been placed.

  In addition, with one set of the 1st groove | channel 11, you may arrange | position the 1st groove | channel 11 to 1 set at equal intervals.

FIG. 6 is a detailed view of the connecting shell 20.
The connecting shell 20 is a hollow disk-like plate, and a convex portion 21 is provided on the outer peripheral portion. The convex portions 21 are all provided to have an equal width.

  The convex side surface 21 a which is the groove side surface of the convex portion 21 is in surface contact with the second groove side surface 12 a of the second groove 12 of the drum 10. On the side surface of the convex portion 21 on the drum 10 side, an axial support portion 21b that is in surface contact with the straight surface 11a provided on the drum 10 side is provided. The number of the axial support portions 21 b corresponds to the number of the first grooves 11 in the drum 10.

FIG. 7 is a perspective view when the drum 10 and the connecting shell 20 are engaged with each other.
As described above, the drum 10 is provided with a notch at one end of the cylindrical structure to provide the first groove 11 and the second groove 12, and the connecting shell 20 is provided with a notch on the outer periphery to provide a notch protrusion. A portion 21 is provided. The convex portion 21 is engaged with and coupled to the first groove 11 and the second groove 12 of the drum 10.

  Note that a snap ring or the like is not particularly provided at the joint between the drum 10 and the connecting shell 20. This is because the thrust force applied to the third ring gear R3 acts on the output gear Output side, but is not particularly limited.

FIG. 8 is a detailed view of the first groove 11 in the drum 10 in the coupling portion and the convex portion 21 in the connecting shell 20.
In the first groove 11 of the drum 10, the positioning straight surface 11 a and the axial support portion 21 b of the connecting shell 20 are in surface contact.

  Since the groove width of the first groove 11 in the drum 10 is wider than the width of the convex portion 21 of the connecting shell 20, the first groove side surface 11 b of the drum 10 and the side surface of the notched convex portion of the connecting shell 20 when engaged. There is no contact with 21a.

  Since the straight surface 11a is positioned in the axial direction of the drum 10, a certain degree of accuracy is required. Therefore, a machining allowance 11c is provided for machining, and accordingly R is provided in the machining allowance 11c.

  As described above, when the groove width of the first groove 11 is increased, R of the machining allowance 11c in the first groove 11 is larger than r of the machining allowance 11c when the groove width is not expanded. Therefore, if the groove width of the first groove 11 is widened, the axial direction and the rotational force transmitted through the adjacent second groove 12 are applied to the first groove 11 as compared to the case where the first groove 11 is not widened. Stress concentration generated in the machining allowance 11c is alleviated.

FIG. 9 is a detailed view of the second groove 12 of the drum 10 and the convex portion 21 of the connecting shell 20 in the coupling portion.
Since the groove width of the second groove 12 of the drum 10 is substantially the same as the width of the convex portion 21 of the connecting shell 20, the second groove side surface 12 a of the drum 10 and the convex portion of the connecting shell 20 are engaged when meshing. The side surfaces 21a are in surface contact with each other.

Regarding the transmission of the rotational torque, the drum 10 and the connecting shell 20 need only be in surface contact only with the second groove side surface 12a and the convex side surface 21a, and the shape of the second groove concave portion is not limited. Therefore, in the second groove 12 recess 12b, R is provided over the entire recess to ensure strength, and the width becomes narrower toward the groove bottom. Therefore, the convex portion 21 does not enter the R portion of the second groove concave portion 12b.
Therefore, the convex part 21 transmits only the rotational direction torque, and no axial force is applied.

Next, the operation will be described.
In FIG. 8, the positioning straight surface 11 a of the drum 10 and the axial support portion 21 b of the connecting shell 20 are in surface contact, thereby positioning the drum 10 in the axial direction.

  Since the groove width of the first groove 11 is wider than that of the second groove 12, the first groove side surface 11 b of the drum 10 is not in contact with the convex side surface 21 a of the connecting shell 20. Therefore, the first groove 11 in the drum 10 is only positioned in the axial direction and does not bear the rotational torque.

  Further, since the first groove 11 has a wider groove width, the R of the machining allowance 11c in the first groove 11 can be increased compared to the case where the first groove 11 is not provided wide, so that the stress concentration on the machining allowance 11c is alleviated. The stress on one groove 11 is reduced.

  Therefore, stress applied to the machining allowance is reduced, and the thickness of the first groove 11 can be reduced to reduce the weight.

  Further, in the automatic transmission, torque transmission is centered in the rotational direction, and the first groove 11 for axial positioning is not subjected to as much force as the rotational direction.

  Therefore, if the strength capable of withstanding the axial positioning of the drum 10 can be ensured, the number of grooves in the first groove 11 is reduced as much as possible, and the number of grooves in the second groove 12 responsible for rotational torque is increased to improve the strength of the coupling portion. It is effective and leads to cost reduction. Therefore, the number of grooves in the first axial groove 11 is smaller than the number of grooves in the second groove 12.

  In FIG. 9, the second groove side surface 12 a of the drum 10 and the convex side surface 21 a of the connecting shell 20 are in surface contact with each other, and thereby the rotational torque of the drum 10 is transmitted to the connecting shell 20.

  Further, the second groove side surface 12a of the drum 10 and the convex side surface 21a of the connecting shell 20 are in surface contact with each other only in the rotational direction. Therefore, the convex portion 21 of the connecting shell 20 does not come into contact with the second groove concave portion 12b of the drum 10, and the second groove 12 in the drum 10 only transmits torque in the rotational direction and is positioned in the axial direction. Absent.

  Furthermore, since the second groove recess 12b is provided with R over the entire recess, stress concentration generated in the recess due to the transmission of the rotational torque can be reduced.

  Therefore, the second groove 12 does not bear the stress in the axial direction, and the stress provided in the second groove 12 where a large torque is applied in the rotation direction can be relieved by R provided in the second groove recess 12b. Even if the wall thickness is reduced, the strength can be ensured.

  As described above, in the connecting structure of the connecting shell 20 of the automatic transmission, the axial positioning and the transmission of the rotational torque are handled by different parts, so that a thin member can be used while ensuring strength. Can be reduced in weight. Furthermore, the number of straight surfaces 11a for axial positioning can be reduced, which contributes to cost reduction.

Next, the effect will be described.
In the connecting shell coupling structure of the first embodiment, the following effects can be obtained.

(1) By providing the first groove 11 that determines the position of the drum in the axial direction and the second groove 12 that is responsible for torque transmission in the rotational direction, transmission of axial force and rotational torque is borne by different parts. Therefore, the stress applied to each part of the coupling member can be reduced, and the member can be thinned. Therefore, Ru can provide lightweight joint.
In addition, since the groove width of the first groove 11 that is the axial positioning groove is enlarged, the first groove 11 does not contact the convex side surface 21a of the connecting shell 20, and only receives the axial force on the straight surface 11a. Therefore, the first groove 11 is released from the burden of rotational torque. Further, as the groove width is increased, the R of the machining allowance 11c is also increased, and the stress concentration applied to the machining allowance 11c is reduced, so that durability can be improved. Moreover, since the 1st groove | channel 11 can be made thinner, a weight reduction of a coupling part is attained. Moreover, since the number of grooves of the first grooves 11 that are axial positioning grooves can be reduced by relieving the stress imposed on the first grooves 11, the number of axial positioning parts having a straight surface can be reduced and the cost can be reduced. Reduction can be achieved (corresponding to claim 1).

  (2) The second groove side surface 12a on the drum 10 side and the convex side surface 21a on the connecting shell 20 side serve as a rotational torque transmission surface, and the second groove 12 and the convex portion 21 are in contact only with this torque transmission surface and rotate. Because it only handles torque, it is freed from the burden of axial force. In addition, by not taking any axial force, all the recesses of the second groove recesses 12b can be set to R, and the stress concentration associated with rotational torque transmission can be reduced. As a result, the stress applied to the torque transmission part is alleviated and the durability is improved, and the durability is maintained even if the torque transmission part is made thinner. Therefore, it is possible to reduce the thickness of the torque transmission portion, and it is possible to provide a lightweight coupling portion (corresponding to claim 2).

(3) The number of second grooves 12 that are rotational direction torque transmission grooves is larger than the number of first grooves 11 that are axial positioning grooves. That is, by increasing the number of rotationally coupled portions where torque is transmitted, it is possible to reduce the torque shared by the second groove 12 at one location, avoiding an increase in the thickness of the coupled portion and the addition of a reinforcing member. it can. Further, the cost can be reduced by reducing the number of axial positioning portions having a straight surface (corresponding to claim 3 ).

(Other examples)
The best mode for carrying out the present invention has been described based on the first embodiment. However, the specific configuration of the present invention is not limited to each embodiment and does not depart from the gist of the present invention. Any change in the design of the range is included in the present invention.

1 is a schematic diagram illustrating an overall configuration of an automatic transmission according to a first embodiment. 2 is an engagement operation table at each gear stage of the automatic transmission according to the first embodiment. FIG. 3 is a collinear diagram at each shift speed of the automatic transmission according to the first embodiment. 1 is an enlarged cross-sectional view of an overall configuration of an automatic transmission according to a first embodiment. 2 is a detailed view of a drum according to Embodiment 1. FIG. It is detail drawing of the connecting shell of Example 1. It is a perspective view at the time of meshing | engaging the drum and connecting shell of Example 1. FIG. It is detail drawing of the positioning part in the meshing part of the drum of Example 1 and a connecting shell. It is detail drawing of the rotation direction torque transmission part in the meshing part of the drum of Example 1 and a connecting shell.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Engine 2 Torque converter 3 Clutch drum 3a 1st spline part 3b 2nd spline part 4 1st piston 4a Pressing part 5 Support member 6 1st clutch hub 7 2nd clutch hub 8 2nd piston 9 Rotating shaft 10 Drum 11 1st Groove 11a Straight surface 11b First groove side surface 11c Processing allowance 12 Second groove 12a Second groove side surface 12b Second groove recessed portion 20 Connecting shell 21 Convex portion 21a Convex portion side surface 21b Axial support portion

Claims (3)

A drum provided with a large number of cutout grooves by axially cutting off an end portion of a cylindrical outer periphery;
A connecting shell that cuts out the circumferential portion in the radial direction to provide a number of cutout protrusions, and is coupled to the drum;
In the connecting shell coupling structure in which the notch protrusion is engaged with the notch groove,
The cutout groove, possess a positioning groove which determines the axial position of the drum, the torque transmission grooves responsible for torque transmission in the direction of rotation,
The connecting shell coupling structure , wherein a groove width of the positioning groove is wider than a width of the notch projection . The connecting shell connecting structure according to claim 1,
A torque transmission surface is provided on a side surface in the circumferential direction of the torque transmission groove and the notch convex portion,
The connecting structure for connecting shells, wherein the torque transmission groove and the notch convex portion are in contact with each other only on the torque transmission surface. In the connection structure of the connecting shell according to claim 1 or 2 ,
The connecting shell coupling structure, wherein the number of the torque transmission grooves is larger than the number of the positioning grooves.

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