JPS60237227A - Power transmission device - Google Patents

Abstract

PURPOSE:To provide dual functions of differential and rib clutch by interposing first and second clutches between the input member and first and second output members, said clutches disengaging the coupling when the angular speed of the input member becomes smaller than that of the first and second output shafts. CONSTITUTION:First and second output members 7, 9 are disposed in the center of rotation of the case 1, and are rotatably supported to the case 1. The right and left hand side wheel axles are formed integrally with the first and second output members 7, 9, and first and second clutches A, B are disposed between said output members 7, 9. An annular cam 15 is coupled by spline to the inner circumferential surface of the center of the right and left hand halves of the case, and first and second dog clutches 17, 19 having pawls 17a, 19a that oppose pawls 7a, 9a of the first and second output members 7, 9 are rotatably engaged with the first and second output members 7, 9.

Description

DETAILED DESCRIPTION OF THE INVENTION (A) Industrial Application Field The present invention relates to a power transmission device disposed, for example, between the rear axles of a front-wheel drive four-wheel drive vehicle.

(b) Technical background and problems As a conventional power transmission device of this type,
There is one described in Japanese Patent No. 4322.

In other words, a clutch is provided between an input member that receives rotational input and first and second output members consisting of a rotating shaft, and during normal driving, rotational input from the input member is transmitted through both clutches. However, when one wheel is on a muddy ground and the other wheel is on a paved road, the driving force of the input member can be transmitted to, for example, the first output member corresponding to the wheel on the paved road side. Further, when the vehicle is cornering, the clutch on the side corresponding to the increase in the angular velocity of the outer wheel is automatically disengaged, so that, for example, the second output member corresponding to the outer wheel can be idled.

However, in such conventional power transmission devices, unless there is a difference in angular velocity between the first output member and the second output member, the input member and both power members are connected by a clutch. When the engine is installed between the rear axles of a 4-wheel drive and is used for 2-wheel drive driving, the interlock between the engine and the input member can be cut off by disengaging the 2-wheel or 4-wheel switching clutch, but the 1. The propeller shaft is rotated via the second output member and the input member, resulting in extremely large running resistance.

Therefore, this type of power transmission device also requires a hub clutch for the rear wheels.

(C) Purpose of the Invention This invention was devised in view of the above-mentioned conventional problems, and has both the functions of a differential limiting type differential device and a hub clutch that automatically engages and engages, and moreover, The object of the present invention is to provide a power transmission device that can be connected at all times as necessary.

(D) Structure of the Invention In order to achieve the above object, the present invention includes an input member that receives rotational input, first and second output members rotatably supported with respect to the input member, and When the angular velocity of the input member becomes smaller than the angular velocity of the first and second output shafts, the input member and the first output shaft are separately provided between the member and the first and second output members. , the first and second clutches are configured to release the connection with the second output member, and the operating means is capable of manually connecting and operating the first and second clutches.

(E) Example Hereinafter, an example of the present invention will be described in detail based on the accompanying drawings.

FIG. 1 shows an embodiment of the present invention, which is arranged, for example, between the rear axles of a front-wheel drive part-time four-wheel drive vehicle. That is, a case 1 serving as an input member that receives rotational input is rotatably installed in a housing 3 on the vehicle body side via a bearing 5. A ring gear A7 (not shown) is attached (pull) to the flange 2 of the case 1, and this ring gear is engaged with a drive pinion (not shown).

First and second output members 7.9, which are rotatably supported with respect to the case 1, are provided at the center of rotation of the case 1.The left and right wheel axles are provided with the first and second output members 7.9. Part 7.9
It is integrally constructed with.

First and second clutches A and B are provided between the first and second clutches 7 and 9 and the case 1, respectively. Specifically, claws 7a and 9a facing toward the center of the case 1 are formed on the outer peripheral surfaces of the first output members 7 and 9.

On the other hand, as shown in FIG. 2, an annular cam body 15 constituting a cam means is spline-fitted on the inner peripheral surface of the left and right center portions of the case 1. As shown in FIG. 3, a mountain-shaped cam surface 15a is formed. On the outer peripheral sides of the first and second output members 7.9,
First and second dog clutch bodies 17.19 are rotatably fitted. The first and second dog clutch bodies 17 and 19 have claws 7a and 9 of the first and second output members 7 and 9, respectively.
Claws 17a and 19a are formed opposite to a. The molds 7a, 9a and the claws 17a, 19a have inclined surfaces 7b, 9b in the engagement direction.

and L7b and 19b are formed. These slopes 7
b, 9b, 17b, and 19b constitute a cam mechanism for releasing the clutch. 28 is a return spring. Further, an arm bar 29 constituting a brake means together with a brake shoe (described later) is fixed to the outer surface of the first and second dog clutch bodies 17.19.
As shown in the figure, it passes through an arc-shaped long hole 31 provided in the side wall 1a of the case 1 and projects outward from the left and right.

On the other hand, a brake holding frame 33 is provided on the outer peripheral surface of both ends of the case 1.
is fitted to the case 1 so as to be relatively rotatable. As shown in FIG. 5, a brake shoe 35 is fitted into the stepped outer circumferential engagement surface 33a of the brake holding frame 33 so as to be slidable relative to the engagement surface 33a. An annular spring 37 is fitted on the outer circumferential surface of the brake shoe 35, and the brake shoe 35 is pressed against the engagement surface 33a by its pressing force.
is pressed against. A plurality of locking recesses 39 are provided in the inner surface of the brake shoe 35 in the circumferential direction, and the tip of the arm frame 29 is fitted and locked in the locking recesses 39 as shown in FIG. There is.

As shown in FIG. 6, a plurality of engagement protrusions 41 are formed on the base end surface of the brake holding frame 33 at equal intervals on the circumference, whereas on the end surface on the housing 3 side, An engagement receiving portion 43 corresponding to the engagement protrusion 41 is formed. The engaging protrusion 41 is removably fitted into the engaging receiving portion 43, and the brake holding frame 33 is held non-rotatably by the housing 3.

A first operation means 45 for connecting and moving the first and second dog clutch bodies 17 and 19 is provided on the outer periphery of the case 1.
7 and 8. This operating means 45 has a movable body 47 supported movably in the radial direction of the case 1, and the movable body 47 is formed with an inclined surface 47a facing outward in the axial direction of the case 1 within the case 1. has been done. The inclined surface 47a is opposed to the inclined surfaces 17G and 19C formed inside the outer peripheral portions of the first and second dog clutch bodies 17.19. Further, the movable body 47 is formed with an inclined surface 47b facing in the same direction outside the case 1. A portion of the movable body 47 outside the case 1 is fitted into a recess 51 of a slide ring 49 fitted into the case 1. Recess 5
1 has an inclined surface 51 opposite to the inclined surface 47b of the moving body 47.
a is formed.

The slide ring 49 is configured to be movable in the direction of the rotation axis of the case 1, and a protrusion 53 formed on the inner surface of the slide ring 49 is fitted into a groove 55 formed in the case 1 in the direction of the rotation axis. ing.

Further, a circumferential groove 57 is formed on the outer periphery of the slide ring 49, and a fork 59 is engaged with this circumferential groove 57. The fork 59 is fixed to the operating rod 61.
1 is configured so that it can be moved in the direction of movement of the slide ring 49 using an operation lever (not shown).

Next, the operation of the above embodiment will be described.

First, when the vehicle runs in four-wheel drive, the case 1 receives rotational input via a ring gear V (not shown). As the case 1 rotates, the cam body 15 spline-coupled to the case 1 also rotates integrally. As the cam body 15 rotates, the dog clutch body 17.19 connected to the cam body 15 also tends to rotate. However, this dog clutch body 17.19
The brake shoe 35 linked to the arm frame 29 receives frictional resistance from the engaging surface 33a of the brake holding frame 33 and moves to the arm frame 2.
Case 1 and dog clutch body 17.
and rotate relative to each other. This relative rotation causes the cam surface 15a to
The driven concave surface 21 and the driven concave surface 21 are in the state shown on the right side in FIG. 3, and the driven concave surface 21 rides on the cam surface 15a, and the dog clutch body 17.19 moves outward in the left-right direction.

Then, the dog clutch body 17.19 and the winter melons 7a and 17a, 9a and 19a of the first and second output members 7 and 9 are engaged as shown on the right side in FIG. 1. Second clutch A; B.

The signal is transmitted to the left and right axles (not shown) via the first and second output members 7 and 9.

During this four-wheel drive driving, when the vehicle turns a curve, a differential is generated between the inner and outer wheels, for example, the first output member 7 on the inner wheel side.
Since the angular velocity of the case 1 is smaller than that of the case 1, the driving force from the case 1 is continuously transmitted to the inner wheel axle via the dog clutch body 17 while maintaining the above operation. On the other hand, since the angular velocity of the second output member 9 on the outer ring side is greater than the angular velocity of the case 1, the cam body 15 in FIG.
The dog clutch body 19 rotates in the opposite direction to the above. At this time, due to the relative movement between the case 1 and the dog clutch body 19, the cam mechanism for releasing the inclined surfaces 7b, 9b1 and U17b, 19b operates, and the dog clutch body 19 is moved as shown on the left side of FIG. The clutch body 19 is suppressed toward the cam body 15 side. Due to this pressure, the clutch is reliably released even if the pawls 9a and 19a are hard to engage, and the driven concave surface 21 is completely fitted into the cam surface 15a with the help of the bias of the return spring 28.

As a result, a gap is created between the pawl 19a of the dog clutch body 19 and the pawl 9a of the second output member 9 as shown in diagram M1, and the left rear wheel axle becomes in a free rotating state, and the differential between the two rear wheels is absorbed. This allows for smooth curve driving.

In addition, even when one rear wheel, for example the left rear wheel, falls into muddy ground and slips during four-wheel drive driving, the right rear vehicle width is receiving resistance from the road surface, so the first starting point is Since the angular velocity of the j member 7 never becomes greater than the angular velocity of the case 1, the corresponding clutch A remains engaged. Therefore, it is easy to drive on rough roads.

Next, when driving by switching from four-wheel drive to two-wheel drive, a well-known switching device cuts off the power connection between the engine and the rear drive shaft, and rotational input to the case 1 is stopped. On the other hand, the left and right wheels receive driving force from the road surface, causing the first and second output members 7.9 to rotate. Therefore, due to this switching from four wheels to two wheels, the angular velocity of the first and second output members 7°9 becomes larger than the angular velocity of case 1 (ultimately zero), and as a result, as described above, the cam body and dog, clutch body 17. ．． 19 becomes the state shown on the left side of FIG. 3, and both clutches A and B are disengaged.

Therefore, from the first and second output members 7 and 9 to the left and right wheels idle, it is possible to reduce running resistance. In this case, the clutch release cam mechanism reliably releases the engagement between the pawls 7a and 9a and the pawls 17a and 19a, so that there is no variation in the idling of the left and right wheels, and driving stability is improved.

Next, if you wish to use the engine brake on the rear wheel side as well, such as when driving down a steep slope, move the operating rod 61 in the direction of the arrow in FIG. 1 using an operating lever (not shown). By this movement of the operating rod 61, the slide ring 49 also moves in the same direction via the fork 59, and the moving body 47 is moved into the case 1 as shown in FIG. 9 due to the action of the inclined surface 51a and the inclined surface 47b. . Therefore, the first and second dog clutch bodies 17.19 are connected and moved by the action of the inclined surface 47a and the inclined surfaces 17C and 19C. Therefore, both the first and second clutches A and B are connected, and engine braking can also be used on the rear wheel side.

The manual connection of the first and second clutches Δ and B can be released by the operation opposite to the above.

Note that this invention is not limited to the above embodiment. For example, the first and second clutches A, B, etc. may be configured with a cone clutch, a friction multi-plate clutch, a combination thereof, or an electromagnetic clutch. In the case of using an electromagnetic clutch, a sensor is provided to detect when the angular velocity of the first and second output members is higher than the angular velocity of the input member, and the brake means is omitted. The braking means may also be of a hydraulic type. This power transmission device can also be arranged between the front axles. Furthermore, the present invention can be applied to, for example, a Fultam four-wheel drive vehicle, and in this case, the wheels automatically spin when the vehicle decelerates, making it possible to avoid a decrease in the vehicle's retained energy and contributing to improved fuel efficiency.

(F) Effects of the Invention As is clear from the above, according to the configuration of the present invention, it is possible to provide the function of a limited differential differential device and the function of an auto hub. Therefore, when applied to a part-time four-wheel drive vehicle, the hub clutch can be omitted, and when applied to a full-time four-wheel drive vehicle, fuel efficiency can be improved. Furthermore, the input side and the output side can be connected at all times as necessary, and engine braking can also be used.

[Brief explanation of drawings]

Fig. 1 is a sectional view of a differential device showing an embodiment of the present invention, Fig. 2 is a sectional view taken along the line ■-■ in Fig. 1, and Fig. 3 shows a cam connection portion between a dog clutch body and a cam body. Detailed cross-sectional view, Figure 4 is a cross-sectional view taken along the ■-■ line in Figure 1, and Figure 5 is the
6 is a sectional view taken along the line Vl-Vl in Fig. 1, Fig. 7 is a sectional view taken along the line ■-■ in Fig. The line arrow sectional view and FIG. 9 are action explanatory views. 1... Case (input member) 7... First output member 9... Second output part A...
First clutch B...Second clutch 17...First dog clutch body 19...Second dog clutch body 29...Arm frame (braking means) 35...Brake (braking means) 45... Operating means 2nd session 1 Figure 3 Figure 4 Figure 5

Claims (1)

[Claims] (1) An input member that receives rotational input, first and second output members rotatably supported with respect to the input member,
When the angular velocity of the input member separately provided between the input member and the first and second output members becomes smaller than the angular velocity of the first and M2 output members, the input member and the first . A power transmission device comprising: first and second clutches for releasing the connection with the second output member; and operating means for manually connecting and operating the first and second clutches. (2) The first and second clutches have first and second dog clutch bodies that can move relative to the first and second output members to intermittent claw engagement, and the input member and the first and second dog clutch bodies. cam means for connecting and moving the first and second dog clutch bodies and engaging them in the rotational direction by relative rotational displacement with the two dog clutch bodies; and cam means for applying resistance in the rotational direction to the first and second dog clutch bodies. 2. The power transmission device according to claim 1, further comprising brake means for applying a brake, and wherein said operating means connects and moves said first and second dog clutch bodies.