JPH04254042A - Power transmission - Google Patents

Abstract

PURPOSE:To obtain a power transmission enabling the shortening of the whole length in the axial direction of an input shaft. CONSTITUTION:A differential gear 39 is provided on an input shaft 23, and the input element 40 of the differential gear 39 is connected to the input shaft 23. Output transmission members are disposed on both sides of the differential gear 39, and both output transmission members are connected to the output elements 43, 44 of the differential gear 39. One of the output transmission members is to be a sprocket 49, and the other output transmission member 81 (76) and the input element 41 of the differential gear 39 can be connected to each other on the outer peripheral side of the differential gear 39 through a locking means 50.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device.

0002

[Prior Art] For power transmission devices, there is a
As shown in Publication No. 359, a differential device is disposed on the input shaft in a state where the input element of the differential device and the input shaft are coupled, and output transmission members are provided on both sides of the differential device. one of the output transmission members is a sprocket, the sprocket is provided with an extension extending toward the input element of the differential, and the extension and the There is one in which the input element of the differential device can be coupled via a locking means. In this, the differential gear can be brought into a differential lock state by coupling the extension portion and the input element of the differential gear by means of a locking means.

However, in recent years, there has been a desire to make devices in general more compact, and even in the power transmission device described above, it is desirable to make the power transmission device more compact, especially to shorten the overall length of the input shaft in the axial direction. It has been demanded.

0004

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and its object is to shorten the overall length of the input shaft in the axial direction in the above-mentioned power transmission device.

[0005]

[Means for Solving the Problems] In order to achieve the above object, the present invention provides a differential device on the input shaft in a state where the input element of the differential device and the input shaft are coupled. output transmission members are disposed on both sides of the differential gear in a state connected to an output element of the differential gear, one of the output transmission members is a sprocket, and at least one of the output transmission members In a power transmission device in which one of the input elements of the differential device can be coupled via a locking means, the input element of the differential device and the other of the output transmission members are connected to the outer periphery of the differential device. The configuration is such that the device can be coupled at the side via the locking means. With the configuration of the first invention described above, by disposing the locking means on the outer peripheral side of the differential, the locking means that was previously disposed between the differential and the sprocket,
Not only can the length of the extension portion be shortened, but also the input element of the differential and the other output transmission member can be coupled via a locking means, thereby selectively obtaining a differential lock state of the differential. While ensuring this, it is possible to eliminate layout restrictions caused by locking means and the like on the sprocket side, and the sprocket can be moved closer to the differential gear. Therefore, the total length of the power transmission device can be shortened in the axial direction of the input shaft.

[0006] In order to achieve the above-mentioned object, the present invention also includes a bevel gear mechanism type differential device on the input shaft in which the pinion shaft of the differential device and the input shaft are coupled. output transmission members are disposed on both sides of the differential gear in a state connected to side gears of the differential gear, one of the output transmission members is a sprocket, and at least one of the output transmission members In a power transmission device in which one of the differential cases and the differential case of the differential device can be coupled via a locking means, the differential case of the differential device and the other of the output transmitting members are connected to the outer peripheral side of the differential device. The structure is such that it can be coupled via the locking means. The configuration of the second invention described above produces the same effect as the first invention described above.

In order to achieve the above-mentioned object, the present invention is characterized in that the sprocket is formed with a recess into which the differential gear can fit. With the configuration of the third aspect of the invention described above, the sprocket can be further moved and disposed toward the differential gear. Therefore, the total length of the power transmission device can be further shortened in the input axial direction.

[0008] In order to achieve the above-mentioned object, in the present invention, in claim 2 or 3, the other side of the output transmission member is an inner peripheral portion of the multi-disc clutch type differential limiting means. and the locking means is capable of coupling an outer circumferential portion of the differential limiting means and a differential case of the differential device in addition to coupling an inner circumferential portion of the differential limiting device with a differential case of the differential device. The configuration is set to do this. According to the fourth invention described above, not only the same effect as the first invention described above is produced, but also the locking means can be used as a means for determining the operation of a differential limiting means other than the differential locking mechanism in addition to the differential locking mechanism. will be possible. Therefore, the total length of the input shaft in the axial direction can be reduced compared to the case where the differential limiting means has its own locking means.

Further, in order to achieve the above-mentioned object, in the present invention, the output element of the differential device and the inner circumferential portion of the multi-disc clutch type differential limiting means are coupled, and the input element of the differential device The element and the inner periphery of the differential limiting means, and the input element of the differential and the outer periphery of the differential limiting means can be coupled via one locking means on the outer periphery of the differential. It is said that there is a structure. With the configuration of the fifth invention described above, the lock means can be used not only as a differential lock mechanism but also as an operation determining means for a differential limiting means other than the differential lock mechanism. Therefore, the total length of the input shaft in the axial direction can be reduced compared to the case where the differential limiting means has its own locking means.

[0010] Furthermore, in order to achieve the above-mentioned object, the present invention is configured such that in claim 5, the differential device is constituted by a bevel gear mechanism. The configuration of the sixth invention described above also produces the same effect as the fifth invention described above.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described, taking as an example the case where the present invention is applied to a four-wheel drive vehicle. In FIG. 1, 1 is a four-wheel drive vehicle, and in the four-wheel drive vehicle 1, an engine 2
, transmission 3, and transfer (power distribution device) 4 sequentially,
It is connected. A rear wheel drive shaft 5 and a front wheel drive shaft 6 are respectively connected to the transfer 4. The rear wheel drive shaft 5 is connected to the rear wheels 8 via a rear differential 7, and the front wheel drive wheels 6 are connected to the rear wheels 8 via a front differential 9. power is transmitted to the front wheels 10.

As shown in FIG. 2, the transfer 4 mainly includes a housing case 12 and 13 consisting of two parts.
The storage cases 12 and 13 are connected in series, and a storage space 20 is formed inside the storage cases 12 and 13.

A high/low speed switching device 21 is disposed in the housing space 20, as shown in FIG. The high/low speed switching device 21 includes a first transmission shaft 22, a second transmission shaft 23 as an input shaft arranged in series with the first transmission shaft 22,
It is generally composed of a planetary gear unit 91 and a switching mechanism 25, and the high/low speed switching device 21 is configured to be able to switch between two high and low speed change mechanisms.

The first transmission shaft 22 is rotatably supported by the side wall 15 of the storage case 12 via a bearing 26, and one end thereof (the left end in FIG. 2) extends outside the storage case 12. The other end (right end in Figure 2) is the storage case 1.
It extends within 2. An output shaft (not shown) of the transmission 3 is connected to one end of the first transmission shaft 22, and power from the transmission 3 is input to the first transmission shaft 22. There is. Note that 115 is a bearing retainer.

The second transmission shaft 23 has one end thereof (FIG.
The middle, left end) is fitted into the first transmission shaft 22, and the other end (right end in FIG. 2) extends toward the side wall 18 of the storage case 13. One end of this second transmission shaft 23 and the first
A bearing 28 is interposed between the transmission shaft 22 and the transmission shafts 22 and 23, so that the transmission shafts 22 and 23 can rotate relative to each other. In this embodiment, one end of the second transmission shaft 23 extends to the bearing 26 position, and a bearing 28 is interposed between the first and second transmission shafts 22 and 23 there. This makes it possible to increase the support strength of the second transmission shaft 23 (so-called strength against swinging) by utilizing the strength of the side wall 15 and the bearing 26, and as a result, the first,
The thrust bearing that receives the force in the axial direction of the second transmission shafts 22, 23 is omitted, and the lengths of the first and second transmission shafts 22, 23 in the axial direction are shortened.

The planetary gear unit 91 is shown in FIG.
As shown, it has a sun gear 92, a ring gear 93, a plurality of planet gears 94, and a carrier 95. The sun gear 92 is integrally provided at the other end of the first transmission shaft 22, and the sun gear 92 is configured to input the power of the first transmission shaft 22. Ring gear 93 is sun gear 9
The plurality of planet gears 94 are located concentrically with respect to the sun gear 9 and fixed to the housing case 12 .
2 and a ring gear 93. career 95
The carrier 95 rotatably supports the plurality of planet gears 94, and the carrier 95 outputs the power input from the sun gear 92 via the planet gears 94.

The switching mechanism 25 is configured such that the first transmission shaft 22
A gear portion 96 provided on the carrier 95 and a tooth portion 97 provided on the carrier 95 are connected to a gear 98 spline-coupled to the second transmission shaft 23, and the axial center of the first transmission shaft 22 is controlled by an operation system (not shown). The connecting sleeve 99 selectively connects the teeth 96 and the gear 98 or the teeth 97 and the gear 98. This switching mechanism 2
5, when the tooth portion 96 and the gear 98 are coupled by the coupling sleeve 99, the first transmission shaft 22 and the second transmission shaft 23
are directly connected to obtain a high speed stage, and when the tooth portion 97 and gear 98 are coupled by the coupling sleeve 99, the speed is reduced by the planetary gear unit 91 to obtain a low speed stage.

As shown in FIG. 2, the accommodation space 20 includes:
A center differential 39 as a differential device is provided. The center differential 39 is provided on the second transmission shaft 23, and in this embodiment, the center differential 39 includes a pinion shaft 40 as an input element and a differential case 4 as an input element.
1, a pair of pinions 42, and a pair of side gears 43 and 44 as output elements. The pinion shaft 40 is connected to the second transmission shaft 23.
The pinion shaft 40 is connected to extend outward in the radial direction of the transmission shaft 23, and the power of the second transmission shaft 23 is input to the pinion shaft 40. The differential case 45 has a substantially hemispherical shape and is disposed on the planetary gear unit 91 side, and the differential case 41 is supported by the tip of the pinion shaft 40. In this embodiment, the differential case 41 and the tip of the pinion shaft 40 are supported by the differential case 41.
A fitting groove 100 is formed in the fitting groove 1, and a pinion shaft 40 having a tip corresponding to the fitting groove 100 is fitted therein. A pair of pinions 42 are rotatably supported by the pinion shaft 40, and both pinions 42 are opposed to each other. A pair of side gears 43 and 44 are meshed with each of the pinions 42, and the power input from the pinion shaft 40 is
Via the pinion 42, it is distributed to one side gear 43 and the other side gear 44. One of the side gears 43 is provided integrally with the rotating cylinder 45, and the second transmission shaft 2 is provided on the inner periphery of the rotating cylinder 45.
3 are fitted together so that they can rotate relative to each other. The other side gear 44 connects the first output shaft 46 to one end (
The other end of the first output shaft 46 (the right end in FIG. 2) passes through the side wall 18 of the storage case 13 and is provided outside the storage case 13. The front wheel drive shaft 6 is connected to the other end. In this case, a bearing 47 is provided on the side wall 18 of the storage case 13, and when the first output shaft 46 passes through the side wall 18, the first output shaft 46 is rotatably supported by the bearing 47. Note that 101 is a bearing retainer. Further, the second transmission shaft 23 enters into one end of the first output shaft 46, and a bearing 48 is interposed between the one end of the first output shaft 46 and the second transmission shaft 23. ing.

As shown in FIG. 2, in the accommodation space 13, a sprocket 49, which is one of the output transmission members, is located between the high-low speed switching device 21 and the center differential 39 and adjacent to the center differential 39. It is arranged. This sprocket 49 is spline-coupled to the outer periphery of the rotating cylinder 4, and a recess 72 is formed in the radially inner portion of the sprocket 49. The center differential 39 (differential case 41) is deeply inserted into this recess 72, and the outer peripheral portion of the sprocket 49 is located on the outer peripheral side of the center differential 39 (differential case 41).

As shown in FIG. 2, the accommodation space 20 includes the center differential 39 and the side wall 18 of the accommodation case 13.
A hub 81 as the other output transmission member is provided between the two. This hub 81 is formed into a substantially hemispherical shape by utilizing a half portion of a conventional substantially spherical differential case, and its inner peripheral portion 102 is spline-coupled to the outer periphery of the second transmission shaft 23 . Inner peripheral portion 102 of this hub 81
has one end (left end in FIG. 2) in contact with the back surface of the other side gear 44, and the other end (in FIG. 2,
The right end) is in contact with the inner race 78 of the bearing 47, and this inner peripheral portion 102 allows the other side gear 44 to
is restricted from moving toward the bearing 47 side.

As shown in FIG. 2, the storage cases 12 and 13 are arranged such that the connecting portion of the two cases 12 and 13 is located on the radially outer side (lower side in FIG. 2) of the second transmission shaft 23. The chain case portion 54 is formed by extending toward the chain case portion 54 . A second output shaft 55 is rotatably supported at the tip of the chain case portion 54 in a state parallel to the first and second transmission shafts 22 and 23.
A sprocket portion 56 is integrally provided to face the sprocket 43. A chain 51 is wound around the sprocket portion 56 and the sprocket 49, so that power is transmitted from the sprocket 49 to the second output shaft 55. The front wheel drive shaft 6 is connected to this second output shaft 55 .

As shown in FIG. 2, a differential lock mechanism 50 is provided on the outer circumferential side of the center differential 39 as a locking means. The differential lock mechanism 50 includes a tooth portion 84 integrally provided on the outer periphery of the differential case 41, a tooth portion 83 integrally provided on the outer periphery of the hub 81, and a first and second It consists of a differential lock sleeve 53 which is movable in the axial direction of the transmission shafts 15 and 16 and connects and disconnects the toothed portions 83 and 84. In this differential lock mechanism 50, when the teeth 83 and 84 are coupled by the differential lock sleeve 53, the differential lock state of the center differential 39 is obtained, and when the teeth 83 and 84 are not coupled by the differential lock sleeve 53, the differential lock state of the center differential 39 is obtained. The dynamic state can be obtained.

Therefore, in this embodiment, since the differential lock mechanism 50 is provided on the outer circumferential side of the differential case 41, it can be made shorter than when the differential lock mechanism 50 is provided adjacent to the differential case 41. Moreover, the differential lock by the differential lock mechanism 50 is performed by the differential case 41.
is coupled to the other side gear 44 via a hub 81 that utilizes a half portion of an existing approximately spherical differential case, and thus the length is newly increased by providing the hub 81. On the other hand, on the sprocket 49 side, there is no restriction on layout by the differential lock mechanism 50. Therefore, the sprocket 49 can be brought closer to the center differential 39, and the second transmission shaft 23
This means that the overall length can be shortened in the axial direction. In particular, in this embodiment, based on the fact that the layout is no longer limited by the differential lock mechanism 50, a recess 72 is formed in the sprocket 49, and the center differential 39 is inserted into the recess 72. This makes it possible to further reduce the overall length.

FIG. 3 shows another embodiment. In this other embodiment, the same components as those in the previous embodiment are given the same reference numerals, and the explanation thereof will be omitted. This embodiment shows a case in which the present invention is applied to a power transmission device equipped with a viscous coupling 74 as a differential limiter in place of the hub 81 of the previous embodiment. That is, in this embodiment, a viscous coupling 74 is provided between the other side gear 44 of the center differential 39 and the bearing 47 as the other output transmission member. This viscous coupling 74 is an existing one, and its configuration is similar to that of the outer piece 7.
5 and an inner piece 76 that is rotatable relative to the outer piece 75 form a case 77, and a large number of disc-like plates and silicone oil are sealed inside the case 77. This viscous coupling 7
The inner piece 76 of No. 4 is spline-coupled to the second transmission shaft 23, and both ends thereof are in contact with the back side of the other side gear 44 and the inner race 78 of the bearing 47.
Movement of the other side gear 44 toward the bearing 47 is restricted. In addition, this inner piece 76 has a tooth portion 1.
03 is integrally provided, and the tooth portion 103 extends toward the outer circumference of the differential case 41 and is positioned adjacent to the tooth portion 84 on the outer circumference of the differential case 41. on the other hand,
Teeth 85 are also provided on the outer periphery of the outer piece 75 of the viscous coupling 74. This tooth portion 85 is provided on the center differential 39 side of the viscous coupling 74. A differential lock sleeve 5 is disposed on the teeth 84 and 85.
3 are arranged. This differential lock sleeve 53 is
As shown in FIG. 3, the differential lock sleeve 53 is formed in a stepped shape, and while the differential lock sleeve 53 always connects the teeth 84 and 85, it is slid by an operation system (not shown) to
4 and 103 into a coupled/uncoupled state. Therefore, when the teeth 84 and 103 are in an uncoupled state, even in that state, the differential lock sleeve 53 connects the teeth 84 and 85, so the differential state of the center differential 39 can be obtained. On the other hand, from the predetermined state, a differential restriction state is obtained by the viscous coupling 74, and when the teeth 84 and 103 are coupled by the differential lock sleeve 53, a differential lock state is obtained. Of course, when the teeth 84 and 103 are in a coupled state, the teeth 84 and 85 are in a non-coupled state, and when the teeth 84 and 103 are in a non-coupled state, the teeth 84 and 85 are in a coupled state. You can also set it as follows.

Therefore, in the above embodiment, the viscous coupling 74 originally provided is used as the other output transmission member, and the viscous coupling 74
Since the differential case 41 and the differential lock sleeve 53 are connected to each other via the differential lock sleeve 53, the overall length of the second transmission shaft 23 in the axial direction can be shortened, as in the embodiment described above. Moreover,
By using one differential lock sleeve 53, it is possible to select between a differential lock and a differential of the viscous coupling 74, and the overall length of the viscous coupling 74 is shortened compared to the case where the viscous coupling 74 has its own lock sleeve or the like. This means that it will be possible to improve the Moreover, since the lock sleeve and the like unique to the viscous coupling 74 are omitted, the number of parts can also be reduced.

[0026]

As described above, in the first to sixth inventions, the total length of the input shaft can be shortened in the axial direction. Moreover, in the third to sixth inventions, the degree of shortening can be further increased compared to the first and second inventions.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing a four-wheel drive vehicle to which an embodiment of the present invention is applied.

FIG. 2 is a sectional view showing a transfer according to an embodiment of the present invention.

FIG. 3 is a sectional view showing a transfer according to another embodiment.

[Explanation of symbols]

4 Transfer 23 Second transmission shaft 39 Center differential 40 Pinion shaft 41 Differential case 43 One side gear 44 Other side gear 49 Sprocket 72 Recess 81 Hub 50 Differential lock mechanism 74 Viscous coupling 76 Inner piece

Claims (6)

[Claims] 1. A differential device is provided on an input shaft with an input element of the differential device coupled to the input shaft, and an output transmission member is provided on both sides of the differential device. one of the output transmission members is a sprocket, and at least one of the output transmission members and the input element of the differential device can be coupled via a locking means. The power transmission device is characterized in that the input element of the differential device and the other of the output transmission member can be coupled via the locking means on the outer peripheral side of the differential device. Power transmission device. 2. A bevel gear mechanism type differential device is provided on the input shaft with the pinion shaft of the differential device coupled to the input shaft, and output transmission members are provided on both sides of the differential device. is disposed in a state connected to a side gear of the differential, one of the output transmission members is a sprocket, and at least one of the output transmission members and a differential case of the differential are connected via a locking means. In the power transmission device, the differential case of the differential device and the other of the output transmission members are connectable to each other via the locking means on the outer peripheral side of the differential device. A power transmission device featuring: 3. The power transmission device according to claim 2, wherein the sprocket is formed with a recess into which the differential gear can fit. 4. In claim 2 or 3, the other of the output transmission members is an inner circumferential portion of a multi-disc clutch type differential limiting means, and the locking means is an inner circumferential portion of the differential limiting means. The power transmission is characterized in that, in addition to coupling the outer peripheral part of the differential limiting means to the differential case of the differential gear, the outer peripheral part of the differential limiting means can be coupled to the differential case of the differential gear. Device. 5. An output element of a differential device and an inner peripheral portion of a multi-disc clutch type differential limiting means are coupled, and an input element of the differential device and an inner peripheral portion of the differential limiting device are connected to each other. A power transmission device characterized in that an input element of a differential device and an outer circumferential portion of the differential limiting means can be coupled via one locking means on an outer circumferential side of the differential device. 6. The power transmission device according to claim 5, wherein the differential device is constituted by a bevel gear mechanism.