JPH0243650B2 - - Google Patents

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a transfer device used in four-wheel drive vehicles, and in particular to a transfer device suitable for construction vehicles, wheel loaders, rough terrain cranes, jeeps, etc. Regarding equipment.

(Prior Art) Conventionally, some of these types of vehicles have been equipped with an auxiliary transmission to supplement the gear ratio of the main transmission, a switching mechanism between four-wheel drive and two-wheel drive, and a differential. It is configured to distribute power to the front wheel drive shaft and the rear wheel drive shaft via a mechanism. When driving on rough terrain, such a vehicle can be operated in four-wheel drive mode by keeping the sub-transmission in a low gear range. Further, in a high gear range, the differential can be locked (inactive) in a place where the tires are likely to slip, and can be activated in a place where the tires are not likely to slip. Furthermore, in the high gear range, the vehicle can be operated in two-wheel drive mode to improve fuel efficiency.
In this way, the above-mentioned vehicle has the advantage that it can be operated in an optimal state according to the driving conditions and the like.

However, in conventional vehicles, the various mechanisms mentioned above are provided separately, resulting in a problem that the structure of the entire device becomes complicated and large, and the cost increases.

(Object of the Invention) The present invention compactly configures a transmission mechanism, a differential lock mechanism, and a switching rotation between two-wheel drive and four-wheel drive, and by combining the operating states of these mechanisms, various driving modes can be realized. The purpose is to provide a transfer device that can meet these conditions.

(Structure of the Invention) The present invention arranges a front wheel drive shaft and a rear wheel drive shaft concentrically, provides a planetary gear mechanism around the shaft, provides a rotational force introduction part in the carrier of the planetary gear mechanism, and a position in which a sun gear is fixed to one of the shafts, a ring gear of the planetary gear mechanism is connected to an input portion of a dog clutch, and a connecting portion of the dog clutch is selectively connected to the input portion with respect to both shafts;
The shafts are configured to be switchable between a position where the shafts are connected to each other and disconnected from the input section, and a planetary gear supported by a carrier of the planetary gear mechanism has teeth in mesh with the sun gear and the ring gear, and teeth on the auxiliary shaft. the auxiliary shaft is arranged concentrically with the two shafts and rotatable relative to them; the auxiliary shaft is provided with an auxiliary dog clutch different from the dog clutch; an auxiliary shaft side member provided on the dog clutch so as to be non-rotatable relative to the auxiliary shaft;
The present invention is characterized in that a stationary member is provided with a fixed member that is not relatively rotatable, and a connecting portion that releasably connects the auxiliary shaft side member to the fixed member.

(Embodiment) In FIG. 1, a housing assembly is formed by bolting covers 2 and 3 to the front and rear ends of the main body of the housing 1, respectively, and a front wheel drive shaft 5 and a rear wheel drive shaft 6 are installed inside the housing assembly. They are arranged concentrically and extending in the longitudinal direction of the vehicle body. The shaft 5 extends from the inside of the cover 3 to a position slightly forward of the cover 2, and its front portion is supported by a front end wall boss of the cover 2 via a bearing 7, and is connected via a joint 8 fixed to the front end. Not connected to front wheel drive mechanism. The shaft 6 extends from the inside of the cover 3 to slightly behind the cover 3, and its middle portion is supported by the rear end wall boss of the cover 3 via a bearing 9, and is supported by a joint 10 fixed to the rear end. It is connected to a rear wheel drive mechanism (not shown). The shaft 6 has a small diameter portion 11 at its front end, and the outer periphery of the small diameter portion 11 fits into the inner periphery of a hole at the rear end of the shaft 5 via a bush 12.

A planetary gear mechanism 15 is provided around the shaft 5 inside the housing 1 . The annular carrier 16 of the planetary gear mechanism 15 has a gear 17 (rotational force introduction part) on its outer periphery, and the gear 17 meshes with an output gear of a transmission (not shown). The carrier 16 includes a cylindrical boss 18 protruding forward from the inner periphery, and the outer periphery of the boss 19 is supported by an annular boss at the front end of the housing 1 via a bearing 14. Rearwardly protruding pins 19 are fixed to a plurality of locations in the circumferential direction of the planetary gear mechanism 15, and a planetary gear 20 is supported around the pins 19 via bushes 21. A sun gear 23 that meshes with the gear 20 is fixed to the outer periphery of the shaft 5 by a spline on the inner periphery. The internal ring gear 25 with which the gear 20 meshes is integrally provided with an inward annular portion 26 near the cover 3, and a cylindrical portion 27 protruding from the inner periphery of the annular portion 26 into the cover 3 is inserted through a bearing 28 on the outer periphery. It is supported by an inner peripheral boss at the front end of the cover 3.

A dog clutch 30 is provided near the rear end of the cylindrical portion 27.
is provided. The input section 31 and output sections 32, 33 of the dog clutch 30 are both formed of annular or cylindrical members, and are arranged in a front-back positional relationship with a bush in between. The input portion 31 is fitted and fixed to the outer peripheral portion of the rear end of the cylindrical portion 27 by an inner peripheral spline. The output portion 32 has a forwardly protruding cylindrical boss 35 fixed to the outer periphery of the rear end of the shaft 5 by spline fitting. The output portion 33 has a rearwardly protruding cylindrical boss 36 fixed to the outer periphery of the front end of the shaft 6 by spline fitting.

The input section 31 and the output sections 32 and 33 each have splines s1, s2, and s3 on their outer peripheries, and a connecting section 37 made of a cylindrical member is provided around them. The connecting portion 37 is provided with a spline on its inner periphery, and this spline is adapted to fit into splines s1, s2, and s3 as described later, depending on the position of the connecting portion 37. The connecting portion 37 has an annular groove 38 on the outer periphery.
A shift fork 40 is fitted into the groove 38. A shift fork 40 is fixed to the front end of a shift rod 41. The rod 41 extends parallel to the shaft 6, and its middle portion is slidably supported in a hole in the cover 3. The rod 41 has an end portion that protrudes outside the cover 3 and is connected to an operating lever via a link mechanism (not shown), for example. 42 are connected. The lever 42 can be switched to four positions A, B, C, and D.

A large gear 45 is integrally formed with the gear 20. The gear 45 is located between the gear 20 and the carrier 16, and its inner periphery is supported by the pin 19 via a bush. The gear 45 meshes with a small diameter gear 48 at the rear end of the cylindrical shaft 46. The shaft 46 is supported on the inner periphery of the boss 18 via a bush 47, and projects further forward than the boss 18. The protruding front end of the shaft 46 is provided with a spline on the outer periphery, and the dog clutch 5 is attached to this spline.
The inner periphery of an annular braked member 51 (lock mechanism) is fitted and fixed by a spline.

The member 51 has a spline 52 on its outer periphery, and a cylindrical connecting portion 53 of the dog clutch 50 is slidably fitted into the spline 52. Connecting part 53
is provided with an annular groove 54 on its outer periphery, and a shift fork 55 is fitted into the groove 54. The fork 55 is fixed to the rear end of the shift rod 56. Rod 5
6 extends parallel to the shaft 5, and the middle part is the cover 2.
The cover 2 is slidably supported in the hole, and an operating lever 57 is connected to the end projecting outside the cover 2 via a link mechanism or the like. The lever 57 can be switched between two positions E and F.
Further, the connecting portion 53 is provided with an external spline 59 on the rear outer periphery, and the spline 59 can mesh with an internal spline 61 of the fixing member 60. The fixing member 60 has an annular shape and is held between the housing 1 and the cover 2 and bolted to the housing 1 and the cover 2.

(Operation) Engine output is transmitted to the carrier 16 via the main transmission, and the gears 20 and 45 always revolve around the shaft 5 together with the carrier 16. According to the above structure, various operating conditions can be set as follows.

(1) Low speed: 4-wheel drive: Differential inoperative (locked), lever position: C, F In this state, the fork 55 has moved the connecting part 53 to the position where it engages with the spline 61, and the fixed member 60 prevents rotation of the shaft 46 via the connecting portion 53 and the member 51, and prevents the shaft 46 from rotating.
The gear 48 of No. 6 is in a non-rotating state. As a result, the rotation of the gear 45 that meshes with the gear 48 is restricted, and the rotation of the gear 23 that is connected to the output shaft 5 is restricted.
rotates at a low speed corresponding to the reduction ratio of the gear ratio of the gear 45 and the gear 48 that meshes with it, and the gear ratio of the gear 20 and the gear 23 that meshes with it. Further, the connecting portion 37 is moved by the shift fork 40 and is removed from the spline s1 of the input portion 31, and is also removed from the spline s1 of the output portions 32 and 33.
2, connect s3. Therefore, the input section 31 is in a freely rotatable state, allowing the gear 25 to rotate freely. In this state, gear 23 to shaft 5
The rotational force transmitted from the output section 32 to the connection section 3
7. It is also transmitted to the shaft 6 via the output section 33. Furthermore, the planetary gear mechanism 15 does not perform a differential function.

(2) High speed: 4-wheel drive: Differential not activated, lever position: B, E In this state, the connecting portion 53 is detached from the fixed member 60, so the shaft 46 is in a freely rotatable state and the gear 48 is No resistance is applied to the rotation of the gear 54. Further, the connecting portion 37 has been moved to a position where the input portion 31 is connected to both the output portions 32 and 33.
The shafts 5 and 6 are integrally connected, and
The gear 25 is also integrally connected to the shaft 6. Therefore, the gear 20 revolves together with the carrier 16 without rotating around the pin 19, and the rotational force transmitted from the carrier 16 to the gear 20 via the pin 19 is transmitted to the shafts 5 and 6 via the gears 23 and 25.

(3) High speed: 4-wheel drive: differential operation,
Positions of the levers 42, 57: D, E Even in this state, the connecting portion 53 is detached from the fixing member 60, so the gear 48 does not apply any resistance to the rotation of the gear 45. The connecting portion 37 connects the input portion 31 to the output portion 33 as shown in the figure.
Gear 25 is connected only to shaft 6.
Therefore, when the front tire and the rear tire rotate at the same speed, such as when the vehicle is running in a straight line, the rotations of both shafts 5 and 6 are the same, so the gear 23 and the gear 2
5 and carrier 16 rotate together. In addition, when a rotation difference between the front and rear tires is required, such as when the vehicle is steering, the action of the planetary gear 20 on the carrier 16 of the input section causes the front wheel drive gear 23 meshing with the planetary gear 20 to The rotation of the rear wheel drive gear 25 changes as necessary. That is, the planetary gear mechanism 15 performs a differential action.

(4) High speed: 2-wheel drive, lever position: A, E Even in this state, the connecting portion 53 is detached from the fixed member 60, so the gear 48 does not apply any resistance to the rotation of the gear 45. The connecting portion 37 connects the input portion 31 only to the output portion 32, and the gear 25 connects only to the shaft 5. Therefore, gear 20 drives shaft 5 via gears 23 and 25,
The shaft 5 rotates at the same speed as the carrier 16. Further, no rotational force is transmitted to the shaft 6.

(Effects of the Invention) As described above, according to the present invention, the planetary gear mechanism 15 is provided around the shaft 5, and the dog clutch 3 is provided to control the operating state of the planetary gear mechanism 15 and the connection state of the shafts 5 and 6.
0 and a dog clutch 50 (lock mechanism) are provided so that the planetary gear mechanism 15 can be used as a differential device or a transmission device that can be switched (released). Also, set the dog clutch 30 to gear 2.
It can be used not only as a connection state control mechanism for the shaft 6, but also as a disconnection device for the shaft 6. Therefore, according to the present invention, a transfer device capable of selecting the various operating conditions described above can be manufactured with a simple structure and at low cost.

In particular, in the present invention, the dog clutch 50 constituting the above-mentioned lock mechanism is constructed as follows and is attached to the planetary gear mechanism 15.

That is, the sun gear 23 and the ring gear 25 are connected to the planetary gear 20 of the planetary gear mechanism 15.
and teeth (gear 47) that mesh with an auxiliary gear 48 provided on the auxiliary shaft (shaft 46), and the auxiliary shaft 46 is arranged concentrically with both shafts 5 and 6 and rotatable relative to them. and auxiliary shaft 46
The above-mentioned dog clutch 50 (auxiliary dog clutch) is attached to the auxiliary dog clutch 50, and an auxiliary shaft side member 51 is provided on the auxiliary shaft 46 so as to be non-rotatable relative to the auxiliary shaft 46;
A fixed member 60 that is provided in a stationary member (housing 1) so as to be relatively unrotatable, and a connecting portion 5 that releasably connects the auxiliary shaft side member 51 to the fixed member 60.
3 are provided.

The dog clutch 50 and the auxiliary shaft 46 act to switch the driving speed between high and low speeds during four-wheel drive, as described in detail above. That is, they constitute a speed switching mechanism, but in the above configuration of the present invention, such a speed switching mechanism can be easily configured by simply adding the dog clutch 50 and the auxiliary shaft 46 to the planetary gear mechanism 15. A speed switching mechanism can be configured with a simple structure.

(Other Embodiments) In Fig. 2, the same parts as those in Fig. 1 are given the same reference numerals, and in the following explanation, only the points that are different from the embodiment in Fig. 1 will be mainly explained. .

In FIG. 2, the shaft 5 is divided at a portion protruding from the shaft 46, and the shaft 5 is formed by two concentric shaft portions 70 and a shaft portion 71. The shaft portion 70 has a hole at the center of the tip portion protruding from the shaft 46, and the small diameter tip portion of the shaft portion 71 is fitted into the inner circumference of this hole via a bush 72.

A dog clutch 75 is provided around the adjacent ends of the shafts 70, 71. One annular member 76 of the dog clutch 75 is spline-fitted to the outer periphery of the distal end of the shaft portion 70, and the other annular member 77 is spline-fitted to the outer periphery of the tip portion of the shaft portion 71.
A spline is fitted to the outer periphery of the tip. Part 7
A cylindrical connecting portion 78 is provided on the outer peripheral spline of 6 and 77.
The inner circumferential splines of are fitted. The connecting portion 78 has an annular groove 79 on its outer periphery, and a fork 80 in the groove 79.
are mated. Fork 80 is fixed to one end of rod 81. At the other end of the rod 81 is a lever 8 that can be switched between two positions G and H.
2 are connected.

According to the above structure, when the lever 82 is set to the position H as shown in the figure, the connecting portion 78 is connected to the member 7.
6 and 77 are connected to each other, and the shaft portions 70 and 71 are integrally connected. Therefore, in this state, by switching to the other levers 42, 57, various operating conditions can be set as in the embodiment shown in FIG.

When the lever 82 is switched to position G, the fork 8 is moved until the connecting portion 78 is detached from the member 76.
Moved by 0. As a result, the shaft portion 71 is separated from the shaft portion 70, and no rotational force is transmitted to the shaft portion 71. In this state, the levers 42, 57
When set to positions D and F, respectively, the driving state can be set to high-speed two-wheel drive. That is, since the lever 42 is in position D, the input section 31 is connected only to the output section 33.
On the other hand, since the lever 57 is in position F, the shaft 46 is fixed unrotatably, and the gear 4
The gear 45 and the gear 21 that mesh with the gear 8 rotate around the pin 19, and the gear 25 is driven not only by the revolution of the gear 20 but also by the rotation of the gear 20. Therefore, the gear 25 is driven at a higher speed than during the high-speed operation shown in FIG.
only is driven at high speed.

By setting the levers 42, 57, and 82 to positions B, E, and G, respectively, medium speed (first
A high speed) two-wheel drive state can be obtained in the structure shown. That is, in position E, the connecting portion 53
is removed from the fixing member 60, the shaft 46 is in a freely rotatable state, and the gear 48 does not provide any resistance to the rotation of the gear 45. In addition, in position B, the connecting portion 37 has moved to the position where the input portion 31 and the output portions 32 and 33 are connected, and the shaft 6 and the shaft portion 7 are connected to each other.
0 is integrally connected to the shaft 6, and the gear 25 is also integrally connected to the shaft 6. Therefore gear 20
carrier 1 without rotating around pin 19.
The rotational force transmitted from the carrier 16 to the gear 20 via the pin 19 is transmitted to the gear 23 and the gear 2.
5 to the shaft 6 and the shaft portion 70. In position G, since the shaft portion 71 is separated from the shaft portion 70, the rotational force transmitted to the shaft portion 70 is not transmitted to the shaft portion 71. Therefore, only the shaft 6 is driven at medium speed.

In any of the above embodiments, a sun gear 48 (external gear) having a different number of teeth meshes with the planetary gear 45, and the rotational speed of the gear 20 is changed by fixing and releasing the gear 45 by the gear 48.
Instead of this structure, an internal ring gear having a different number of teeth may be meshed with the gear 45, and the ring gear may restrict the gear 45 and the gear 20 on the vehicle.

[Brief explanation of the drawing]

FIG. 1 is a schematic cross-sectional view of an embodiment of the present invention, and FIG. 2 is a schematic cross-sectional view of another embodiment. 5... Shaft for front wheel drive, 6... Shaft for rear wheel drive, 15... Planetary gear mechanism, 16... Carrier, 17...
Gear (rotational force introduction part), 20...planetary gear,
23...Sun gear, 25...Ring gear, 30...
... Dog clutch, 31 ... Input section, 37 ... Connection section, 46 ... Shaft (auxiliary shaft), 48 ... Auxiliary gear, 50 ... Dog clutch, 51 ... Auxiliary shaft side member, 53 ... Connection member, 60 ...Fixed member.

Claims (1)

[Claims] 1. A front wheel drive shaft and a rear wheel drive shaft are arranged concentrically, a planetary gear mechanism is provided around the shaft, a rotational force introduction part is provided in the carrier of the planetary gear mechanism, and a sun gear of the planetary gear mechanism is provided on one side of the shaft. The ring gear of the planetary gear mechanism is connected to the input part of the dog clutch, and the connecting part of the dog clutch is set at a position where the input part is selectively connected to the two shafts, and when both shafts are connected to each other, the input part of the dog clutch is connected to the input part of the dog clutch. teeth that mesh with the sun gear and the ring gear, and teeth that mesh with an auxiliary gear provided on the auxiliary shaft. , the auxiliary shaft is arranged concentrically with both shafts and rotatable relative to them, and the auxiliary shaft is provided with an auxiliary dog clutch different from the dog clutch, and the auxiliary dog clutch is arranged to rotate relative to the auxiliary shaft. A vehicle comprising: an auxiliary shaft-side member that is installed in a non-rotatable manner; a fixed member that is installed on a stationary member so that it cannot rotate relative to the stationary member; and a connecting portion that releasably connects the auxiliary shaft-side member to the fixed member. transfer equipment.