JP2001099186A - Clutch structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a tumble of a gear and generation of a vibration, by stably performing an axial direction support of a helical gear engaged with and disengaged from a shaft by a clutch. SOLUTION: This clutch structure is constituted by providing a 3-speed shift driven gear 23 consisting of a helical gear arranged rotatably on a transmission counter shaft 12, hydraulic clutch 33 provided on the transmission counter shaft 12 for engaging a gear 23b with and disengaging it from the counter shaft 12, and a buffer member 60 adjacently to a thrust bearing 65 for rotatably holding this gear 23b in an axial directional prescribed position on the counter shaft 12 to resist against thrust force F generated by the driven gear 23b meshed with a mate drive gear 23a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch structure including a helical gear rotatably disposed on a shaft, and a clutch mechanism for engaging and disengaging the helical gear with the shaft.

[0002]

2. Description of the Related Art The use of a hydraulic clutch or the like for setting a gear position of an automatic transmission has been well known. An automatic transmission using such a hydraulic clutch is disclosed in, for example, JP-A-4-19426 and JP-B-7-45888. In such automatic transmissions, it has been well known that a power transmission mechanism using a helical gear is used for the purpose of improving power transmission efficiency and reducing noise and vibration.

[0003]

Here, when a helical gear is used as a gear engaged with and disengaged from the shaft by a clutch, the helical gear generates a thrust force generated when the helical gear meshes with a mating helical gear to transmit power. It is important that the helical gear is supported stably in the axial direction to prevent the helical gear from falling down and the vibration in the axial direction. In addition,
When the clutch is released and power is not transmitted, the thrust force acting on the helical gear is extremely small,
When the clutch is engaged, a thrust force proportional to the torque transmitted through the helical gear acts. Therefore, the axial support of the helical gear against the thrust force when the clutch is engaged is a particular problem.

Conventionally, in order to suppress the fall and vibration of a helical gear or the like engaged with a clutch, the play between a hub portion of the gear and a clutch disk fitting portion is reduced, or the gear is rotatably supported. It is known that the clearance of the bearing in the radial bearing portion is reduced, or the radial bearing is formed into a bush. However, in such a method, there is a problem that the wear of the gear hub portion and the clutch disc fitting portion causes the helical gear to fall down, vibrate, and the like. And the problem of insufficient lubrication of the bearing portion is likely to occur when the bushing is used.

The present invention has been made in view of the above problems, and has a structure in which a helical gear that is engaged and disengaged from a shaft by a clutch can be stably supported in the axial direction, and the occurrence of gear falling and vibration can be suppressed. It is an object of the present invention to provide a clutch structure.

[0006]

In order to achieve such an object, the present invention relates to a helical gear (for example, in the embodiment) rotatably disposed on a shaft (for example, a transmission counter shaft 12 in the embodiment). In a clutch structure including a third-speed driven gear 23b) and a clutch mechanism (for example, a third-speed hydraulic clutch 33 in the embodiment) provided on the shaft for engaging and disengaging the helical gear with the shaft, the helical gear is connected to the shaft. A thrust bearing portion (for example, the thrust bearing 65 in the embodiment) for rotatably holding at a predetermined position in the axial direction above is provided with a cushioning member that opposes a thrust force F generated when the helical gear meshes with the mating helical gear. A clutch structure is configured.

In the case of such a clutch structure, the thrust force generated when the helical gear is engaged with the shaft by the clutch acts on the shock-absorbing member to reduce the thrust force. Generation of vibration is effectively suppressed. Therefore, the occurrence of transmission torque fluctuation due to the occurrence of the helical gear falling when the clutch is engaged is suppressed, and smooth torque transmission is performed, thereby reducing gear noise. Further, the generation of the axial clearance in the thrust bearing portion can be suppressed by the buffer member, and the helical gear can be stably supported in a no-load state.

The cushioning member can be formed by joining two donut disk-shaped holding plates rotatably disposed on a shaft with an elastic member, thereby providing a desired structure with a simple structure. A buffer member that can achieve the object can be obtained.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. FIG. 2 shows an automatic transmission having a clutch structure according to the present invention. The transmission 10 is provided so as to be coupled to a side end surface of the engine 1, a transmission housing 15 is joined to the engine flywheel housing, and the output shaft 1 a of the engine 1 and the torque converter 5 are connected. For this reason, the output of the engine 1 is transmitted to the transmission input shaft 1 via the torque converter 5.
1 is transmitted. In the transmission housing 15, a transmission input shaft 11 and a transmission counter shaft 12 are arranged in parallel with each other and rotatably, respectively.
A transmission mechanism 20 is disposed between the transmission gears 1 and 12.

The transmission mechanism 20 includes a LOW gear set 21a and 21b meshing with each other, and a second speed gear set 22a and 22b.
Gear set for third speed 23a, 23b, gear set for fourth speed 24
a, 24b and a reverse gear set 25a, 25b. However, the reverse gear set meshes with each other via a reverse idler gear (not shown) for reversing the rotation direction. Drive side gear 2 in each of these gear sets
1a, 22a, 23a, 24a, 25a are disposed on the transmission input shaft 11, and driven gears 21b, 22b,
23b, 24b and 25b are arranged on the transmission counter shaft 12. Among these gears, the LOW drive gear 21a, the second speed drive gear 22a, the third speed driven gear 23b, the fourth speed drive gear 24a, and the reverse driven gear 25b are provided on the transmission input shaft 11 or the transmission counter shaft 12. It is arranged freely when rotating,
The remaining gears are fixed to one of these shafts.

Each of the gears rotatably disposed on any of the shafts as described above has a hydraulic clutch 31 to 3 respectively.
5 are provided. These five hydraulic clutches 31 to
By selectively operating 35, any of the rotatably disposed gears is integrally connected to a shaft on which it is disposed, and power transmission is performed based on a gear set having the gears. . By selectively operating the hydraulic clutches 31 to 35 in this manner, the engine power transmitted to the transmission input shaft 11 is transmitted by a gear set corresponding to the activated hydraulic clutch, and the transmission counter shaft is driven. 12 is transmitted. An output drive gear 16 a is fixed to the transmission counter shaft 12, and the output drive gear 1
6a meshes with an output driven gear 16b fixed to the transmission output shaft 17. Therefore, the transmission counter shaft 1
The engine power transmitted to the output gear set 16
The transmission is transmitted to the transmission output shaft 17 via a and 16b, and then to the drive wheel via the drive shaft 18.

The clutch structure according to the present invention can be used for the hydraulic clutches 31 to 35 in the transmission 10 having the above configuration. A hydraulic clutch employing the clutch structure according to the present invention will be described using a third-speed hydraulic clutch 33 as an example. This hydraulic clutch 33 is shown enlarged and in section in FIG. 1, and has a clutch drum 51 fixed to the transmission counter shaft 12.
The clutch drum 51 has a clutch oil chamber 51a therein, and a clutch piston 52 is provided in the clutch oil chamber 51a.
Are movably fitted in the axial direction. A return spring 53 is disposed opposite to the clutch piston 52. The return spring 53 is provided on the receiving plate 5 whose rightward movement is restricted by a retaining ring 54a.
4 and presses the clutch piston 52 leftward.

A plurality of clutch plates 55 and clutch discs 56 are arranged alternately in the axial direction with a diaphragm spring 52b interposed therebetween at positions where the piston portions 52a of the clutch pistons 52 in the clutch drum 51 face each other. Are closed by the end plate 57 and locked and retained by the retaining ring 58, and are located in the clutch drum 51. At this time, the clutch plate 55 is locked on the clutch drum 51 on the outer peripheral side, and the clutch plate 55
Is movable in the axial direction, but rotates integrally with the clutch drum 51. On the inner peripheral side, the clutch disk 56 is spline-engaged with a clutch spline portion 23c formed integrally with the driven gear 23b for third speed, and the clutch disk 56 is movable in the axial direction, but is displaced in the axial direction. It is configured to rotate integrally with the driven gear 23b.

The transmission counter shaft 12 is provided with a lubricating oil supply path 12a and a clutch operating oil supply path 12b, from which lubricating oil and clutch operating oil are respectively supplied. The clutch operating oil supply passage 12b is connected to a clutch oil chamber 51a via a first passage 51b formed in the clutch drum 51. Therefore, when the clutch operating oil is supplied to the clutch oil chamber 51a, the clutch piston 52 is pressed rightward in FIG. 1 by the oil pressure, and the piston portion 52a presses the clutch plate 55 and the clutch disk 56 against the end plate 57. . As a result, the two plates 55 and 56 are engaged by the frictional force between the two plates 55 and 56, the third speed driven gear 23b rotates integrally with the clutch drum 51, and the power transmission by the third speed gear sets 23a and 23b is performed. The third gear is set. As can be seen from this, a clutch mechanism is constituted by the clutch piston 52, the clutch plate 55, and the clutch disk 56 disposed inside the clutch drum 51.

The third-speed driven gear 23b engaged and disengaged by the clutch mechanism is rotatably held on the transmission counter shaft 12 by the radial bearing 67, and is axially positioned by the thrust bearings 65 and 66. . Here, the thrust bearing 66 is positioned in contact with the side end face of the second speed driven gear 22b fixed to the transmission counter shaft 12, and the thrust bearing 6
5 is a cushioning member 60 disposed on the transmission counter shaft 12.
Is positioned in contact with the side end face of the.

The lubricating oil supply passage 12a is open to the inner peripheral surface of the thrust bearing 65. The lubricating oil supply passage 12a is connected to a lubricating oil supply device (not shown). Spline part 2
It is supplied to the clutch plate 55 and the clutch disk 56 through the left space 3c. The lubricating oil supplied in this way lubricates the engagement surfaces of the clutch plate 55 and the clutch disk 56, so that the heat generating portion is cooled and lubricated by the clutch engagement.

Here, the structure of the buffer member 60 will be described in detail with reference to FIG. This cushioning member 60
As shown in FIG. 3, two donut-shaped holding plates 6
Eight cylindrical elastic members 63 arranged at equal intervals and at the same circumferential position are joined to the holding plate 61 on the inner peripheral side. It is formed to protrude. The reason why the columnar elastic members are arranged at intervals is to take into account the deformation of the elastic members. The stopper 64 is for preventing the elastic member 62 from being excessively compressed and deformed. Cushioning member 60
Is disposed so as to be sandwiched between the receiving plate 54 and the thrust bearing 65, as can be seen from FIG. Thus, the vibration in the axial direction is absorbed by the elastic member 63 of the cushioning member 60, so that the rotation is smooth.

Power transmission by the third speed gear trains 23a and 23b having the third speed hydraulic clutch 33 having the above-described configuration will be described with reference to FIG. The third-speed drive gear 23a coupled to the transmission input shaft 11 is rotationally driven together with the transmission input shaft 11, and the third-speed driven gear 23b that always meshes with the gear 23a is engaged with the third-speed hydraulic clutch 33. And the transmission input shaft 1
1 to the transmission counter shaft 12.
Here, the third-speed drive gear 23a and the driven gear 2
Since 3b is a helical gear, a thrust force (gear reaction force) F acts on the meshing point of both gears when power is transmitted in this manner.

This thrust force F is indicated by an arrow F in FIG.
As shown by, the third gear driven gear 23b acts on the meshing point of the teeth, and the third gear driven gear 23b is acted upon by a rotational moment as indicated by an arrow M. This rotational moment acts in a direction in which the third-speed driven gear 23b is tilted,
When the gear falls in this way, the transmission torque fluctuates, causing vibration and noise of the gear. However,
In the clutch structure of the present embodiment, the shock absorbing member 60 absorbs the moment M against the above-mentioned moment M, thereby preventing the gear from falling down and performing smooth torque transmission. Is suppressed. In particular, the thrust force F greatly fluctuates in the initial stage of engagement of the third-speed hydraulic clutch 33, and tends to act as an axial excitation force on the third-speed driven gear 23b. The thrust bearings 65 and 66 are prevented from acting on the thrust bearings 65 and 66, while being absorbed by the gears 60 and effectively suppressing the gears from falling and vibrating.

In the above, the cushioning member 60 is constituted by joining and holding a plurality of cylindrical elastic members between two holding plates. However, the shape of the elastic member is not limited to this, and the shape of the elastic member is not limited to this. Various shapes are possible. Further, the arrangement position of the cushioning member 60 is not limited to the above-described configuration.
It may be arranged between the speed driven gear 22b.

[0021]

As described above, according to the present invention,
Since the thrust bearing for rotatably holding the helical gear, which is engaged with and disengaged from the shaft by the clutch mechanism, on the shaft is provided with a buffer member that opposes the thrust force generated when the helical gear meshes with the mating helical gear, The thrust force generated when the helical gear is engaged with the shaft by the clutch acts on the cushioning member and is moderated, so that the occurrence of the helical gear falling and vibration during the clutch engagement operation is effectively suppressed. Therefore, the occurrence of transmission torque fluctuation due to the occurrence of the helical gear falling when the clutch is engaged is suppressed, and smooth torque transmission is performed, thereby reducing gear noise. Also, due to the cushioning member,
The generation of axial clearance in the thrust bearing portion can be suppressed, and the helical gear can be stably supported under no load.

The cushioning member can be constituted by joining two donut disk-shaped holding plates rotatably arranged on a shaft by an elastic member, whereby a desired structure can be achieved with a simple structure. A buffer member that can achieve the object can be obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a hydraulic clutch having a clutch structure according to the present invention.

FIG. 2 is a sectional view showing a structure of an automatic transmission in which a shift operation is performed by the hydraulic clutch.

FIG. 3 is a sectional view of a cushioning member constituting the hydraulic clutch.

FIG. 4 is a diagram illustrating power transmission by a third-speed gear train disengaged by the hydraulic clutch.

[Explanation of symbols]

 Reference Signs List 10 automatic transmission 12 transmission counter shaft (shaft) 23b driven gear (helical gear) for 3rd gear 33 hydraulic clutch for 3rd gear 51 clutch drum 52 clutch piston (clutch mechanism) 55 clutch plate (clutch mechanism) 56 clutch disk (clutch mechanism) Reference Signs List 60 buffer member 61, 62 holding plate 63 elastic member 65, 66 thrust bearing (thrust bearing)

Claims (2)

[Claims] 1. A clutch structure comprising: a helical gear rotatably disposed on a shaft; and a clutch mechanism provided on the shaft for engaging and disengaging the helical gear with the shaft. A clutch structure, characterized in that a thrust bearing for rotatably holding the shaft at a predetermined position in the axial direction on the shaft is provided with a cushioning member that opposes a thrust force generated when the helical gear meshes with a mating helical gear. 2. The cushioning member according to claim 1, wherein two donut disk-shaped holding plates rotatably arranged on the shaft are joined by an elastic member. The described clutch structure.