JP2578916Y2 - Power transmission for automatic transmission - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for transmitting power from an engine to a torque converter.

[0002]

2. Description of the Related Art As a torque converter used for an automatic transmission of an automobile or the like, when the speed ratio between a pump and a turbine becomes a predetermined value or less, a so-called direct connection between the pump and the turbine suppresses a reduction in power transmission efficiency. Some have a direct coupling clutch. In the case of an automatic transmission equipped with such a torque converter, when the pump and the turbine are connected by a direct coupling clutch, torsional vibration accompanying the torque fluctuation of the engine is transmitted to the automatic transmission. And is connected to the engine through a power transmission device having

In this type of power transmission device, an input member connected to an engine and an output member connected to a torque converter are assembled so as to be able to rotate relative to each other by a predetermined angle, and these two members are rotated by a compression spring in a rotating direction. The torsional vibration inputted after the engagement of the direct coupling clutch is reduced by the vibration absorbing action of the compression spring generated with the relative rotation of the input member and the output member.

Incidentally, this similar technique is disclosed in, for example,
This is disclosed in, for example, Japanese Patent Publication No. 100653.

[0005]

However, in the case of the conventional power transmission device described above, the natural frequency of the torsional vibration of the engine-power transmission device-torque converter system (hereinafter referred to as the power transmission system) is determined by the engine starting. Since the engine is in the rotation range, a torsional resonance occurs in the power transmission system when the engine is started, thereby increasing the relative rotation between the input member and the output member, and causing a problem that excessive torque is applied to the compression spring, the input member, and the like. When the excessive torque is applied to the components such as the compression spring and the input member in this manner, it tends to cause abnormal noise and fatigue of the member.

Accordingly, the present invention provides a power transmission for an automatic transmission in which torsional resonance is not generated in a power transmission system at the time of engine start, and generation of abnormal noise and member fatigue caused by the torsional resonance can be reliably prevented. It is intended to provide a transmission device.

[0007]

According to the present invention, an input member and an output member are elastically linked in a rotational direction via a compression spring while being fixed to the outer periphery of the input member. A power transmission device for an automatic transmission in which a ring gear with which a starter motor is engaged at the time of engine start is provided, and an output member is connected to a converter housing of a torque converter having a directly-coupled clutch. Attached axially displaceable,
The ring gear and the output member are provided with serrations that can be engaged with each other, and the serration between the ring gear and the output member is engaged by axial displacement of the ring gear accompanying the engagement of the starter motor and the ring gear.

[0008]

When the engine is started, the starter motor is engaged with the ring gear, the ring gear is displaced in the axial direction, and the ring gear and the output member are engaged by serration.
As a result, the input member and the output member are directly connected without the intermediary of the compression spring, and the natural frequency of the power transmission system is out of the rotation range at the time of starting the engine.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to FIGS.

In the drawings, reference numeral 1 denotes a crankshaft of an engine, and a drive plate 2 a as an input member is fixed to an end of the crankshaft 1 together with a reinforcement plate 3 by bolts 4. And
Another drive plate 2b, which forms a pair with the drive plate 2a, is connected to the drive plate 2a at predetermined intervals by stop pins 5 (see FIG. 2). A plurality of leaf springs 6 extending radially outward are attached at equal intervals to the outer peripheral edge of the drive plate 2a.
Is mounted with a ring gear 8 which meshes with a pinion 7 of a starter motor. The leaf spring 6 couples the drive plate 2a and the ring gear 8 so as to be integrally rotatable, and allows relative axial displacement of the drive plate 2a and the ring gear 8 by its elasticity. The ring gear 8 has outer teeth 8a meshing with the pinion 7 on the outer peripheral surface, while serrations 8b are formed on the inner peripheral surface. The pinion 7 of the starter motor has a ring gear 8 when the pinion 7 projects.
A step 7a is formed to abut the end face of the ring gear 8 to displace the ring gear 8 in the axial direction.

Reference numeral 9 denotes an output member formed in a disk shape. The output member 9 has an inner peripheral end 9a supported on the outer peripheral portion of the reinforce plate 3 via a bearing 10, and A plate portion 9b is relatively rotatably accommodated between the pair of drive plates 2a, 2b. A serration 9c is formed on the outer peripheral surface of the output member 9, and when the ring gear 8 is displaced in the axial direction by a predetermined amount, the serration 8b of the ring gear 8 meshes with the serration 9c. A plurality of portions of the plate portion 9b from the outer periphery constitute a converter housing 1 constituting a torque converter 11 of the automatic transmission.
2 is connected to the converter housing 12 by a bolt 13 so that the output member 9 always rotates integrally with the converter housing 12. In addition, a plurality of circumferential grooves 14 are formed at portions from the outer circumferences of the drive plates 2a, 2b so that the heads of the bolts 13 and the projections 15 for coupling the converter housing 12 contact the drive plates 2a, 2b. Not to be. Further, a plurality of windows 16 and a plurality of stopper holes 17 (see FIG. 2) which are curved in the circumferential direction are formed in the plate portion 9b, and nested compression springs 18a, 18b are formed in each window 16. The stop pins 5 are accommodated in a state of being arranged in series, and the stop pins 5 are loosely inserted into the respective stopper holes 17. The stopper hole 17 is provided to avoid interference between the stop pin 5 and the output member 9, and is formed in an arc shape along the circumferential direction so that the output member 9 and the drive plates 2a and 2b can relatively rotate within a predetermined angle range. Is formed.

Reference numeral 19 denotes the output member 9 and the drive plate 2
b, an idler interposed so as to be relatively rotatable with respect to the both, and the idler 19 is a base 1 formed in an annular shape.
9a and a plurality of arms 19b bent from the base 19a toward the output member 9 and protruding radially outward. Each of the arms 19b is accommodated in each window 17 of the output member 9. It is interposed between the springs 18a and 18b. Similar windows 20 and 21 which are curved along the circumferential direction are formed at positions corresponding to the windows 16 of the output member 9 of the drive plates 2a and 2b, respectively. The ends of the compression springs 18a and 18b accommodated in the respective windows 16 come into contact with each other. Therefore, both drive plates 2a as input members,
The output member 2b and the output member 9 are elastically linked in the rotation direction via compression springs 18a and 18b.

Reference numeral 22 denotes a turbine hub of the torque converter 11 spline-fitted to the output shaft 23;
A turbine runner 24 is fixed to the flange portion 22a of the turbine hub 22, and a direct coupling clutch (piston) 25 is fitted to the boss portion 22b so as to be slidable in the axial direction. A plurality of claws 26 are formed on the direct coupling clutch 25, and the claws 26 are engaged with grooves 27 provided on the outer peripheral side of the flange portion 22a. And this direct coupling clutch 25
, When the speed ratio of the pump impeller 28 and the turbine runner 24 is oil pressure P ₁ on the back side of the lockup clutch 25 becomes less than a predetermined value is larger than the oil pressure P ₂ on the front side, the slide to the left side direction in FIG. 1 Thus, it is connected (locked up) to the inner side wall 12 a of the converter housing 12.

With the above configuration, the driving torque of the engine is basically transmitted from the crankshaft 1 to the torque converter 11 and the output shaft 23 through the drive plates 2a and 2b, the compression springs 18a and 18b, and the output member 9. Is transmitted. When the speed ratio between the pump impeller 28 and the turbine runner 24 is greater than a predetermined value, the torsional vibration is reduced mainly by the viscous fluid of the torque converter 11 because the direct coupling clutch 25 does not operate. Impeller 28 and turbine runner 24
If the speed ratio of the direct coupling clutch 2
5, the output member 9 and the converter housing 1
2 is directly connected, the torsional vibration is caused by the drive plate 2
a, 2b and the output member 9 are reduced by the vibration absorbing action of the compression springs 18a, 18b.

At the time of starting the engine, the following is performed.

When the driver moves the ignition switch to the start position when starting the engine, the pinion 7 of the starter motor projects forward and starts rotating.
At this time, when the pinion 7 projects forward, FIGS.
As shown in FIG. 1, the teeth of the pinion 7 mesh with the external teeth 8a of the ring gear 8, and the stepped portions 7a abut on the end faces of the ring gear 8 to elastically deform the leaf spring 6 to move the ring gear 8 in the axial direction (in the figure). (To the right). When the ring gear 8 is displaced in the axial direction, the serrations 8b of the ring gear 8 mesh with the serrations 9c of the output member 9, and the drive plate 2a as an input member is connected to the output member 9 without passing through the compression springs 18a, 18b. Is done. For this reason, the natural frequency of the power transmission system in the torsional direction is increased, and the power transmission system is out of the rotation range at the time of starting the engine.
Therefore, at this time, torsional resonance does not occur in the power transmission system, and the vibration level-engine speed characteristic at the time of engine start is as shown by a chain line in FIG. still,
The solid line in FIG. 6 shows the vibration level-engine speed characteristics when a conventional power transmission device is used.

Then, when the ignition switch is moved to the ON position, the ring gear 8 returns to the original position with the retraction of the pinion 7, and the ring gear 8 and the output member 9
The connection by the serrations 8b and 9c is released.

[0018]

As described above, according to the present invention, the ring gear is attached to the input member so as to be displaceable in the axial direction, and the ring gear and the output member are provided with serrations which can be engaged with each other. Due to the axial displacement of the ring gear, the serrations of the ring gear and the output member are engaged, so that when the engine is started, the input member and the output member are directly connected, and the natural frequency of the torsional vibration of the power transmission system is reduced when the engine starts. Out of range,
No torsional resonance occurs in the power transmission system. Therefore, generation of abnormal noise and member fatigue due to the torsional resonance can be reliably prevented.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view taken along the line BB of FIG. 2 showing one embodiment of the present invention.

FIG. 2 is a partially broken side view showing the same embodiment.

FIG. 3 is an enlarged sectional view of a portion A of FIG. 1 showing the same embodiment.

FIG. 4 is an enlarged sectional view of a portion A in FIG. 1 showing the embodiment.

FIG. 5 is an enlarged sectional view of a portion A in FIG. 1 showing the same embodiment.

FIG. 6 is a graph showing vibration level-engine speed characteristics of the present invention and a conventional one.

[Explanation of symbols]

 2a: Drive plate (input member), 8: Ring gear, 9: Output member, 8b, 9c: Serration, 11: Torque converter, 12: Converter housing, 18a, 18b: Compression spring, 25: Direct coupling clutch.

Continuation of the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F02N 15/02-15/06 F02B 77/00 F16F 15/12 F16H 41/24

Claims (1)

(57) [Scope of request for utility model registration] An input member and an output member are elastically linked in a rotational direction via a compression spring. On the outer periphery of the input member, a ring gear with which a starter motor is engaged when the engine is started is provided. In a power transmission device of an automatic transmission, which is coupled to a converter housing of a torque converter having a built-in direct coupling, a ring gear is attached to the input member so as to be axially displaceable, and the ring gear and the output member are engaged with each other. A power transmission device for an automatic transmission, wherein a possible serration is provided, and the serration between the ring gear and the output member is engaged by an axial displacement of the ring gear accompanying the engagement of the starter motor and the ring gear.