JPS6159044A - Differential motion limiter - Google Patents

Abstract

PURPOSE:To attempt reduction of the size of a bearing by interposing a reaction plate and a thrust bearing in the direction of a drive shaft between a housing and the portion subjected to clamping reaction caused by a clutch clamping means. CONSTITUTION:The reaction of a clamping force due to a hydraulic piston 18 acting on friction clutches 13, 13' and the action of a cam is arranged to be absorbed by a housing 1 via a reaction plate 14', a needle bearing 15' and a space 16'. Accordingly, the reaction of clutch clamping force caused by a clutch clamping means is arranged to be absorbed by a reaction plate and a thrust bearing and thereby the bearing used for supporting a differential case can be miniaturized.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a differential limiting device equipped with clutch engagement means for applying engagement force to a friction clutch.

(Prior art) As a conventional differential limiting device, for example, Japanese Patent Application Laid-Open No. 53-45
The one described in Japanese Patent No. 832 is known.

This conventional device includes a differential case that is rotatably supported by a tapered roller bearing in a housing, a pair of side gears that are provided with left and right drive shafts, and that are disposed facing each other inside the differential case, and a pair of side gears that are arranged opposite to each other inside the differential case. It was equipped with a friction clutch disposed between the differential case and a clutch engagement piston, which was provided on the friction clutch and applied clutch engagement force using hydraulic pressure from the outside.

(Problems to be Solved by the Invention) However, in such a conventional device, the reaction force of the clutch engagement force by the clutch engagement means is transmitted through the differential case and the Taber Cora bearing that rotatably supports the differential case. Since the structure was such that the housing absorbs the thrust force, the tapered roller bearing receives both the +r force (support for the thrust force of the differential case) and the engagement reaction force of the friction clutch, and the small tapered roller bearing lacks supporting force. There was a problem in that the tapered roller bearing became larger.

(Means for Solving the Problems) That is, the present invention has been made for the purpose of solving the above-mentioned problems, and in order to achieve this purpose, the present invention provides a housing that is rotatably supported by the housing. a differential case, a pair of side gears which are provided with left and right drive shafts, and which are arranged to face each other inside the differential case; a friction clutch which is disposed between the side gears and the differential case; In the differential limiting device, the differential limiting device includes a clutch engagement means that is provided on a friction clutch and applies a re-launch engagement force using fluid pressure from the outside, between the housing and the engagement reaction force acting part by the clutch engagement means. , a reaction plate 1, and a thrust bearing were interposed in the direction of the drive shaft.

(Function) Therefore, in the differential limiting device of the present invention, the reaction force of the clutch engagement force by the clutch engagement means can be absorbed by the housing via the reaction plate and the thrust bearing.

(Example) Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

In describing this embodiment, a differential limiting device for an automobile will be taken as an example.

First, the configuration of the first embodiment shown in FIGS. 1 and 2 will be explained.

Reference numeral 1 denotes a housing, which is supported by a stud port 2 on the vehicle body side, and this housing 1 is composed of a front housing 1a, a rear housing 1b, and a piston housing 1c.

Reference numeral 3 denotes a differential case, which is rotatably supported with respect to the housing 1 by a tapered roller bearing 4.4'. It is made up of.

The differential case 3 includes a ring gear 7 that meshes with a pinion gear 6 provided on the propeller shaft 5.
is provided, and the rotational driving force from the propeller shaft 5 is transmitted to the differential case 3.

Reference numeral 8.8' denotes a side gear, which is disposed opposite to each other inside the differential case 3.A left drive 11i1+9 and a right drive 6h9' are provided on the side gears 8, 8' by spline connection. It will be done.

A pinion mate shaft 10 is disposed between the side gears 8 and 8', and a pinion mate gear 11 that meshes with the side gear 88' is supported on the pinion mate shaft 10.

12. 12' is pressure ring, and slide f'? of the differential case 3 is applied. This pressure ring 12.12 is provided in a fitted state with M3c.
' is fixed in the rotational direction by fitting into the slide groove 3C and is provided so as to be slidable in the axial direction.

In addition, this pressure ring l2, l2' has the following:
As shown in FIG.
' is formed and is brought into contact engagement with a V-shaped cam portion 10a formed at the end of the pinion gear shaft 10.

Reference numeral 13.13' denotes a friction clutch, which is disposed between the pressure rings 12, 12' and the differential case 3.
' is a multi-plate clutch structure, and friction plates 13a, 13a fixed to the differential case 3
' and friction discs 13 b and 13 b' fixed to the side gear 8.8'.

14, l4' is a reaction plate disposed in contact with the outer surface of the friction clutch 13.13', and this reaction plate 14.14'
The axial protrusions 14a and 14a' are inserted through the opening 3d of the differential case 3 and attached to the differential case 3.

Note that the reaction brakes 14 and 14' rotate together with the differential case 3.

15.15' is a needle bearing as a thrust bearing, and the above-mentioned rear axis type plate 14.14'
One needle bearing 15 is interposed between the spacer 16.16' and the spacer 16.16'.
The other needle bearing 15' is supported in the housing 1 via a bushing rod 17 and a hydraulic piston 18.
is supported by the housing 1 via a spacer 16'.

Reference numeral 18 denotes a hydraulic piston as a clutch fastening means, which is disposed in the housing 1 so as to be able to reciprocate in the axial direction.A bushing rod 17 is provided on one end surface of the hydraulic piston 18, and a bush rod 17 is provided on the other end surface. A pressure oil chamber 19 and a hydraulic boat 20 are provided. Reference numeral 21 denotes a working hydraulic system, which supplies working hydraulic pressure to the hydraulic piston 18, and this working hydraulic system 21
includes a motor 23 that drives the hydraulic pump 22, a pressure oil pipe 25 that supplies pressurized oil from the reserve tank 24 pressurized by the hydraulic pump 22 to the hydraulic boat 20, and a pressure oil pipe 25 provided in the middle of the pressure oil pipe 25. check valve 26
and a relief valve 28 that releases the pressurized oil flowing through the pressure oil pipe 25 to the reserve tank 27 when the pressure is higher than a predetermined pressure, and a switch between supplying the pressurized oil to the hydraulic boat 20 side or returning it to the reserve tank 27. A pressure switch 30 is provided on the pressure oil pipe 25, and a controller 31 controls the operation of the motor 23, the solenoid valve 29, and the pressure switch 30.

The hydraulic system 21 is operated by the motor 23 when the switch is turned on. The solenoid valve 29 and the pressure switch 30 are operated, and from then on, the hydraulic boat 20 is controlled to be supplied with pressurized oil at a predetermined pressure.

Next, the effect will be explained.

(B) When driving on a general road When driving on a general road, the hydraulic piston 18 is not operated by keeping the hydraulic system 21 switched off, but the normal differential restriction can be maintained even if the hydraulic piston 18 is not operated. Due to the device structure, differential limiting action can be obtained.

That is, the pressure ring 12, 12' is pushed open left and right by the cam action with the pinion mate shaft 10, presses the friction discs 13b, 13b' and the friction plates 13a, 13a', and presses the friction clutch 1.
3.13' is coupled, and by this clutch action, it is possible to transmit a larger torque to the non-idling (fixed side) wheel than the torque transmitted to the idling wheel.

This characteristic is shown in graph A in Figure 3,
Graph B shows the characteristics without a differential limiting device, and the same torque is transmitted to the left and right wheels regardless of whether they are on the fixed side or on the idling side.

In addition, the force R that pushes the pressure ring 12.12' open is expressed by R=Q, Co50 (0: component force in the slope direction of the reaction force F against the force trying to turn the pressure ring, 0: slope angle). (See Figure 2), this force R becomes the engagement force of the friction clutch 13, 13', and its reaction force is:
It is absorbed in the housing 1 via the reaction plate 14.14' and the needle bearings l5, l5'.

Therefore, due to the differential limiting action described above, when the vehicle turns and there is a rotation difference between the left and right wheels, the torque of the lower speed wheel increases, resulting in understeer characteristics, and the driving force of the vehicle is reduced by the differential limiting action. It increases compared to without, and the driving performance of the vehicle improves.

(b) When traveling straight on a highway, etc. When traveling straight on a highway, etc., straight-line stability is particularly required, so when the operating hydraulic system 2 is turned on, pressurized oil is supplied from the hydraulic boat 20. After entering the chamber 19, the hydraulic piston 18 is moved to the right in FIG. 1, and the friction clutch 13 is pressed to engage the clutch, and the reaction force also pushes the friction clutch 13' to engage the clutch.

Therefore, the friction clutch 13.13 due to the aforementioned cam action
In addition to the fastening force of ', the hydraulic piston 18 applies a fastening force to the friction clutches 13 and 13', so the differential limiting effect becomes even greater, and when driving straight ahead, there is a change in road surface conditions or if one wheel lifts. Even if such a situation occurs, a sudden drop in driving force can be suppressed, and stable straight-line driving can be achieved without wobbling or the like.

The torque characteristic when the hydraulic system 21 is turned on has a characteristic in which the magnitude of the initial torque differs depending on the set pressure, and the graph shows the characteristic line drawn within region C in Fig. 3. be.

In addition, the reaction force of the fastening force due to the hydraulic piston 18 and cam action acting on the friction clutch 13, 13' is absorbed by the housing 1 via the rear crayon plate 14', needle bearing 15', and spacer 16'. .

(c) When one wheel enters mud, etc. If one wheel enters mud, sand, or other area with a low coefficient of road friction, the switch on the hydraulic system 2' should be turned off in the same way as in (b) above. When engaged, a larger torque is transmitted from the high-speed wheels (wheels that have entered the blinds, etc.) to the low-speed wheels (wheels that have escaped) in proportion to the engagement force of the friction clutch J, 3.13'. This makes it easier to escape, and it is also easier to drive on roads with a low coefficient of friction.

Note that the case where the operating hydraulic system 21 is turned on and the engagement force of the friction clutch 13, 13' is strengthened by external hydraulic pressure to obtain a large differential limiting action is not limited to the above-mentioned case, but it is also possible to judge the driving situation. You may do so as appropriate.

Next, a second embodiment shown in Fig. f34 and Fig. 5 will be described.

This embodiment includes a pinion mate shaft 10 whose end has a square cross section, and a square groove 12b that engages with the square cross section 10b.
, 12b', pressure ring L 2 , 12'
This is an example using the hydraulic piston 18, in which the engagement force to the friction clutches l 3 and 13' is not generated by the cam action as in the first embodiment, and the differential limiting action is obtained entirely from the hydraulic piston 18. Note that the other configurations are the same as those of the first embodiment, so the drawings are omitted.

Therefore, the torque characteristic diagram in the second embodiment is as shown in FIG. 5, and can be appropriately set within a range depending on the set pressure of the hydraulic pressure device 21.

Although the embodiments of the present invention have been described above in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the present invention may be modified without departing from the gist of the present invention. included.

For example, the flange fastening means is not limited to the hydraulic piston structure as in the embodiment, but may be a means of other structures.

(Effects of the Invention) As described above, according to the differential limiting device of the present invention, the reaction force of the clutch engagement force by the clutch engagement means is absorbed by the reaction plate and the thrust bearing. This has the effect that the bearing supporting the can be made smaller.

In addition to the above-mentioned effects, in the first embodiment, it is not necessary to constantly supply fluid pressure from the outside to perform differential restriction, and the frequency of use of fluid pressure can be suppressed. Even if the supply equipment fails, it can be used as a normal differential limiting device.

[Brief explanation of drawings]

1 is a sectional view showing a differential limiting device according to the first embodiment of the present invention, and FIG. 2 is a view taken from the direction of arrow Z in FIG. 1, 733
The figure is a torque characteristic diagram of the i1 embodiment device, FIG. 4 is a diagram showing the pinion mate shaft and pressure ring of the second embodiment device of the present invention, and FIG. 5 is the torque characteristic diagram of the second embodiment device. . 1...Housing 3...Differential case 8.8'...Side gear 13.13'...Friction clutch 14, l 4...Reaction plate 15.
15'... Needle bearing (thrust 4i1 + receiver) 18... Hydraulic piston (flanch fastening means) Patent application Nissan Motor Co., Ltd. Figure 2

Claims (1)

[Claims] 1) A differential case rotatably supported by a housing, a left and right drive shaft are provided, a pair of side gears are disposed facing each other inside the differential case, and a pair of side gears are disposed between the side gears and the differential case. In the differential limiting device, the differential limiting device includes a friction clutch provided therein, and a clutch engagement means provided in the friction clutch that applies a clutch engagement force by external fluid pressure. A differential limiting device characterized in that a reaction plate and a thrust bearing are interposed in the drive shaft direction between the force acting part and the force acting part.