JPH02286944A - Differential device - Google Patents

Abstract

PURPOSE:To prevent loss of torque and stabilize performance by providing an electromagnet to support an attraction member on the fixing side, attract it and move a clutch member to one of two positions of joint and release and an energizing member to move the clutch member to the other side. CONSTITUTION:When an electromagnet 77 is electrified, a clutch member 47 is pushed by an operation member 57 to the left and a joint part 49 starts clawing. At this time, if there is a rotary difference between a differential case 19 and a side gear 43, thrust force due to the difference of pressure angles theta1, theta2 works to the left, the joint part 49 is joined with the pressure force of the electromagnet 77 and this thrust force so that the clutch member 47 is stably held at this joint position. Additionally, at this time, an attraction member 63 is constrained magnetically by the electromagnet 77 and sliding is taken place between the attraction member 63 and a base part 61 of the operation member 57. Consequently, the electromagnet 77 and the attraction member 63 do not relatively rotate and no loss of magnet and no heating is generated, and the characteristics of the electromagnet 77 are not deteriorated and the differential lock performance is stabilized.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a differential device having a differential lock mechanism.

(Prior art) JP-A-63-195449 describes a "sliding differential limiting gear assembly." As shown in FIG. It includes a multi-disc clutch 105 for motion restriction, an electromagnet 109 supported by an external housing 107 on the fixed side, and an operating member 111 that rotates integrally with the case 101 and is attracted by the electromagnet 109 to engage the multi-disc clutch.

In this way, since the operating member 111 is arranged on the rotating side and rotates relative to the electromagnet 109, the magnetic force becomes rotational resistance of the case 101, causing torque loss. Further, the performance of the electromagnet 109 deteriorates due to heat generation due to loss of magnetic force, and the differential III limit function becomes unstable. Furthermore, when the operating member 111 and the M magnet 109 come into contact when they are attracted, rotational resistance and heat generation will further increase due to their sliding rotation, which will exacerbate the above-mentioned problems and reduce durability due to wear.

(Problems to be Solved by the Invention) Therefore, an object of the present invention is to provide a differential device that has no torque loss, stable performance, and excellent durability.

[Structure of the Invention] (Means for Solving the Problems) The differential device of the present invention includes a differential case that rotates by inputting torque, a differential gear set that rotates in conjunction with the differential case, and an output gear of this differential gear set. a clutch member that is movable between a connecting position and a disconnecting position with the differential case; an operating member that integrally penetrates the differential case and has one end in contact with the clutch member; and a clutch member that is slidable with the other end of the operating member. an electromagnet that is supported on the stationary side and that attracts the suction member and moves the clutch member to one of the two positions via the operating member; and an urging member that moves the clutch member to the other position. It is characterized by

(Function) When the differential case rotates due to torque input, this rotation is differentially distributed via the differential gear set and its output gear.

When the clutch member is moved to the connected position by the attraction or urging member of the electromagnet, the differential case and the output gear are connected so that they cannot rotate relative to each other, so the differential rotation between the output gears is stopped and a differential lock state is established, which reduces the torque distribution ratio between them. are equal. When the clutch member moves to the release position, the differential lock is released and the differential distribution function as described above is restored.

While the electromagnet is in operation, the attraction member is restrained by magnetic force and hardly rotates, and sliding occurs between the attraction member and the operating member. Therefore, unlike the conventional example, there is no torque loss due to rotational resistance of magnetic force, and performance does not become unstable due to heat generation. Further, since the force mainly applied to the sliding portion is only the biasing force of the biasing member, the sliding portion suffers less wear and has excellent durability.

(Example) One embodiment will be explained with reference to FIG. 1 and FIG. 2.

This embodiment is used in the power system of the vehicle shown in FIG.

Hereinafter, the left and right directions will be referred to as the left and right directions in FIG. 1, and the upper side thereof corresponds to the front (above) of the vehicle in FIG. 2. Also, members that are not numbered are not shown.

The vehicle in Figure 2 includes an engine 1, a transmission 3, a direction changing gear set 5, a propeller shaft 7, a V-differential 9 (differential device in this embodiment), and a rear axle 11.13.
, left and right rear wheels 14.15, left and right front wheels 16.17, etc.

As shown in FIG. 1, the differential case 19 of the rear differential 9 is rotatably supported on the differential carrier 21 by bearings 23,25. The differential carrier 21 rotatably supports a drive pinion shaft 29 whose front end is connected to the propeller shaft 7 side and whose rear end is integrally formed with a drive pinion gear 27. A ring gear 31 meshing with this gear 27 is fixed to the differential case 19 with bolts 33, and is rotationally driven by the driving force from the engine 1.

A binion shaft 37 is fitted into an axial groove 35 provided on the inner periphery of the differential case 19 and is supported so as to rotate together with the differential case 19 . A pinion gear 39 is rotatably supported on the pinion shaft 37, and a pair of side gears 41, 43 (output gears) mesh with the left and right sides of the pinion gear 39.

The left rear axle 11 is spline-coupled to the left side gear 41, and the right rear axle 13 is spline-coupled to the right side gear 43. The axle tube 45 of the rear axle 11 is attached to the left end of the differential carrier 21, and the axle tube of the rear axle 13 is attached to the right end. In this way, a differential gear set 46 is constructed.

Therefore, due to the driving force from the engine 1, the differential case 19
rotates, this rotation is transmitted through the pinion shaft 37 and the pinion gear 39, and when the pinion gear 39 rotates, the rotation is transmitted from each side gear 41° 43 to the left and right rear wheels 14.1.
It is differentially distributed to the 5 side. A ring-shaped clutch member 47 is disposed between the right side gear 43 and the differential case 19 so as to be movable in the axial direction. Connecting portions 49 and 51 (meshing portions) are provided between the clutch member 47, the side gear 43, and the differential case 19, respectively. The clutch member 47 is constantly engaged with the right connecting portion 51 and moves from side to side to engage and disengage the left connecting portion 49. When the side gear 43 and differential case 19 are moved to the left (connection part @) as shown in the lower half of FIG. Become. Further, when the side gear 43 and the differential case 19 are moved to the right (to the uncoupled position) as shown in the upper half of FIG. In addition, as shown in FIG. 1(b), the connecting portions 49, 51
Each meshing pressure angle θ1. θ2 is θ2>θ1.

A retaining ring 53 is attached to the inner circumference of the differential case 19, and a clutch member 4 is provided between the retaining ring 53 and the clutch portion 47.
A return spring 55 (
(biasing member) is attached.

The operating member 57 includes a plurality of axial arms 5 arranged in the circumferential direction.
The arm 59 extends through the differential case 19 and its left end abuts against the clutch member 47. A ring-shaped suction member 63 is fitted into the differential case 19 so as to be relatively rotatable, and is slidably abutted on the right side of the base portion 61 of the operating member 57 . Retaining rings 65 and 67 are mounted on the differential case 19 to restrict the movement range of the operating member 57 and the suction member 63.

A rotation prevention member 69 is attached to the differential carrier 21 by a bolt 71 to prevent rotation of the lock nut 73 of the bearing 25.
This rotation preventing member 69 prevents the electromagnet 77 and the attraction member 63 from rotating. The electromagnet 77 attracts the suction member 63 to the left and moves the clutch member 47 to the connected position via the operating member 57. electromagnet 7
7 is configured to be operable manually from the driver's seat or automatically in accordance with steering conditions or road surface conditions.

When the electromagnet 77 is energized, the clutch member 47 moves to the operating member 5.
7 and moves to the left, and the connecting portion 49 begins to mesh. At this time, if there is a rotational difference between the differential case 19 and the side gear 43, a thrust force due to the difference in pressure angles θ1θ2 acts to the left, and the connecting portion 49 is connected by the pressing force by the electromagnet 77 and this thrust force, and the clutch member 47 is stably held in this connected position. Further, at this time, the attraction member 63 is restrained by the electromagnet 77 by magnetic force, and sliding is performed between the attraction member 63 and the base portion 61 of the operating member 57.

In this way, unlike the conventional example, the electromagnet 77 and the suction member 6
3 do not rotate relative to each other, and no loss of magnetic force or heat generation occurs, the characteristics of the electromagnet 77 are not deteriorated and the differential lock function is stabilized.

Further, since the rotation restraining force of the electromagnet 77 is not applied to the rotation side, no torque loss occurs. Furthermore, since the force applied to the sliding portion during suction is a small amount obtained by subtracting the thrust force from the biasing force of the return spring 55, there is little wear and excellent durability.

Also, since this thrust force is input to the pinion gear 39 via the side gear 43, the pinion shaft 3 is
7 moves to the left along the groove 35, and each backlash is always kept equal at these meshing portions.

When the energization to the electromagnet 77 is stopped, the return spring 5
5, the clutch member 47 returns to the disengaged position. Note that the biasing force of the return spring 55 is made larger than the thrust force due to the pressure angle θ2 of the connecting portion 51.

When the differential lock is released, the vehicle can turn smoothly due to the differential rotation of the left and right rear wheels 14,15.

When the differential is locked, this differential rotation is stopped, improving straight-line stability and transmitting the same driving force to each rear wheel at all times, so only one rear wheel slips on rough roads, improving drivability. never lose.

In addition, in this invention, the differential gear set may be of a planetary gear type. Furthermore, the relationship between the coupling and disengaging positions of the clutch member and the attracting direction of the electromagnet and the biasing direction of the biasing member may be freely selected. Further, the pressure angle of the clutch member may be large on the left side and small on the right side, or may be made equal.

[Effects of the Invention] As described above, the differential device of the present invention does not cause torque loss due to magnetic force, has stable performance without loss of magnetic force, and has excellent durability.

[Brief explanation of drawings]

FIG. 1(a) is a cross-sectional view of one embodiment, and FIG. 1(b) is a cross-sectional view of one embodiment.
), FIG. 2 is a skeleton mechanism diagram showing the dynamic horn system of a vehicle using this embodiment, and FIG. 3 is a sectional view of a conventional example. 19...Differential case 46...Differential gear set 4
7...Clutch member 57...Operation member 63
...Attraction member 77...Electromagnet agent
Patent Attorney Hidekazu Miyoshi

Claims (1)

[Claims] A differential case that rotates by inputting torque, a differential gear set that rotates in conjunction with the differential case, a clutch member that is movable between a connection position and a disconnection position between the output gear of the differential gear set and the differential case, and the differential case. an operating member that integrally rotates through the body and has one end in contact with the clutch member side; a suction member that slidably contacts the other end of the operating member; A differential device comprising: an electromagnet that moves the clutch member to one of the two positions; and an urging member that moves the clutch member to the other position.