JP2003336721A - Gear plate type actuator, and power interrupting device and differential device using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To achieve compactness in an axial direction while enlarging an operation stroke. <P>SOLUTION: Plates 15, 17 and 19, an electric motor to operate the plate 17 to rotate, and a cam mechanism 21 to convert rotation of the plate 17 into operation force to move the plate 19 are provided. The cam mechanism 21 is provided diametrically inward or the plate 15. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear plate type actuator for operating an operated device such as a clutch, a power connection / disconnection device for connecting / disconnecting the driving force by the clutch, and a connection / disconnection for the driving force by the clutch, or , A differential device for limiting differential.

[0002]

2. Description of the Related Art Japanese Patent Publication No. 5-54574 discloses a differential device 1001 as shown in FIG.

The differential device 1001 is housed in a differential carrier 1003, and the outer differential case 1
005, an inner differential case 1007, a bevel gear type differential mechanism 1009, a dog clutch 1011 and a pneumatic actuator 1013.

The meshing clutch 1011 includes a clutch ring 1015 movably splined to an inner differential case 1007 and an outer differential case 1005.
It is formed between and.

The actuator 1013 is a differential carrier 1
Cylinder 1017 and piston 101 fixed to 003
The air pressure is supplied from an air pump driven by the engine to operate the piston 101.
The clutch ring 1015 is moved through the gear 9 and the shift fork 1021 to engage the dog clutch 1011. When the supply of air pressure is stopped, the meshing of the dog clutch 1011 is released.

The outer differential case 1005 is rotationally driven by the driving force of the engine input via the drive pinion gear 1023 and the ring gear 1025.

When the meshing clutch 1011 meshes,
The outer differential case 1005 rotates through the inner differential case 1007 and the differential mechanism 1009 to rotate the axle 102.
It is distributed from 7,1029 to the left and right wheels, and the vehicle enters the four-wheel drive state, and the running performance, the escape performance, and the stability on a bad road are improved.

When the meshing clutch 1011 is disengaged, the parts from the inner differential case 1007 to the left and right wheels are separated from the engine side, and the vehicle becomes 2
The wheels are driven, and the fuel efficiency of the engine is improved.

In addition to the fluid pressure type actuator such as the pneumatic actuator 1013, there is an actuator which converts the rotational torque of the electric motor into the operating force of the operated device such as a clutch by a cam mechanism.

In this actuator using an electric motor, unlike a device using a fluid pressure type actuator,
It does not require a pump, its drive source, or a pressure line, and has a simple structure, low cost, a small installation space, light weight, and excellent in-vehicle performance. In addition, it has a fast response and high reliability. There are advantages.

[0011]

In the case of a meshing clutch in which the meshing teeth move in the axial direction and are intermittent, unlike the friction clutch, it is necessary to greatly move the meshing teeth in the axial direction (tooth height direction). An actuator that operates the dog clutch requires a large operation stroke.

On the other hand, in an in-vehicle device such as the differential device 1001, if the operation stroke of the actuator is increased, the actuator becomes large in the axial direction and the in-vehicle performance may be deteriorated.

Further, in the differential device 1001 using the actuator 1013, the shift fork 10
A shift mechanism including 17 is required, the number of parts is large, the structure is complicated, and it is expensive.
Air pumps account for about 30% of these costs.

Further, in a fluid pressure type actuator such as a pneumatic actuator, it is difficult to avoid pressure leakage in the pressure line, and this pressure leakage reduces the response of engagement and disengagement of the meshing clutch 1011 to reduce the running condition. It becomes difficult to quickly switch between the four-wheel drive state and the two-wheel drive state according to the change.

Further, in addition to the decrease in reliability due to this pressure leak, in order to prevent the pressure leak, it is necessary to take measures such as strengthening the seal of each part of the pressure line, which results in an increase in cost. Is hard to avoid.

Further, the pneumatic actuator 1013
Is easily affected by the internal pressure and the external pressure, the operation becomes unstable, and the performance tends to deteriorate.

Further, when the fluid pressure type actuator is used, a wide disposing space including the piping of the pressure line and its routing space and the like is required, so that the differential device 1001 becomes large and the vehicle mountability deteriorates. In addition, it is necessary to change the casing (for example, the differential carrier) that houses the differential device 1001, resulting in a large change cost and further reducing the vehicle mountability.

Therefore, according to the present invention, a gear plate type actuator which has a compact structure in the axial direction while having a sufficiently large operation stroke for the operated device and has a simple structure, low cost and high reliability, It is an object of the present invention to provide a power disconnecting device and a differential device configured by using this gear plate type actuator.

[0019]

According to another aspect of the present invention, there is provided a gear plate type actuator comprising: an annular supporting plate fixed to a stationary side; and a cam arranged on one axial side of the supporting plate so as to be rotatable in the forward and reverse directions. A plate, a movable plate that is axially movable on the other side of the support plate in the axial direction, and that moves and operates the operated device, and a gear provided on the gear plate on the cam plate side. A gear set, an electric motor that rotates the cam plate in the forward and reverse directions via the gear set, and a cam plate are provided between the cam plate and the movable plate. And a cam mechanism for converting into a moving operation force, wherein the cam mechanism is provided on the radially inner side of the support plate.

According to the gear plate type actuator of the first aspect, the cam mechanism is provided on the radially inner side of the support plate, whereby not only the axial overlapping dimension of the cam mechanism and the support plate is reduced, but also the following claims: As in the items 2 and 3, the axial overlapping dimension of the cam mechanism, the cam plate and the movable plate is reduced, so that the assembly of the support plate, the cam plate and the movable plate is made compact in the axial direction.

Therefore, the stroke of the movable plate can be increased by that amount, and the dog clutch, which requires a large operation stroke, can be moved and operated with a sufficient stroke amount.

Further, if the axial dimension reduction value due to the compactness is distributed to both the operation stroke amount and the compactness, a device using a gear plate type actuator (for example, a power source) can be obtained while obtaining a large operation stroke amount. The intermittent device and the differential device) can be made compact in the axial direction to improve the vehicle mountability.

Further, the gear plate type actuator of the present invention for converting the rotational torque of the electric motor into the operating force of the operated device by the cam mechanism is different from the conventional example using the fluid pressure type actuator in that an expensive pump or fluid is used. No pressure actuator (piston and cylinder), shift mechanism, etc. are required, the number of parts is small, the structure is simple, and it can be implemented at low cost.

Further, in the system using the fluid pressure type actuator, the function deterioration due to the pressure leakage which is inevitable is released, the reliability is greatly improved, and the seal of each portion of the pressure line is strengthened and the cost is accordingly increased. Can be avoided.

Further, unlike a system using a pneumatic actuator, since it is not affected by pressure fluctuation, the performance is improved and stabilized.

Further, unlike the fluid pressure type actuator, since a wide arrangement space such as a pressure line and a space around the pressure line is not necessary, the gear plate type actuator and the operated device can be made lighter and more compact. In-vehicle performance is greatly improved.

Further, it becomes unnecessary to change the casing for accommodating the actuator and the operated device, and a large increase in cost due to the change can be avoided.

A second aspect of the present invention is the gear plate type actuator according to the first aspect, wherein the movable plate has an axial portion formed at a radial end of the base portion,
A protrusion formed of a radial portion formed on the axial portion is provided, and the support plate and the cam plate are arranged axially inward of the base portion and the radial portion of the movable plate, A cam mechanism includes the radial portion of the movable plate and a cam surface provided on the cam plate and in contact with the radial portion.

According to the second aspect of the invention, the support plate and the cam plate are arranged axially inward of the radial portion of the protrusion provided on the movable plate and the base portion. As described above, the cam mechanism supports the support plate. By being provided on the inner side in the radial direction, the axial dimension of the base portion and the projection (radial portion) of the movable plate is significantly reduced, and the same operation and effect as the configuration of claim 1 can be obtained.

A third aspect of the present invention is the gear plate type actuator according to the first or second aspect, wherein the cam plate is provided with a support projection that surrounds and supports an inner peripheral end portion of the support plate. It is provided, and the cam mechanism is provided radially inward of the support protrusion.

According to the third aspect of the invention, the cam plate is provided with the support protrusions surrounding and supporting the inner periphery (end portion) of the support plate, and the cam mechanism is provided radially inside the support protrusions. Since the support protrusion of the cam plate and the cam mechanism are prevented from overlapping with each other and the axial dimension is reduced, the same operation and effect as those of the configuration of claim 1 or 2 can be obtained.

According to a fourth aspect of the present invention, there is provided a power connecting / disconnecting device according to any one of the first to third aspects, wherein a pair of torque transmission members and a clutch arranged between the torque transmission members are operated. A gear plate actuator serving as a device is provided, and the torque is interrupted between the torque transmission members by operating the clutch by the gear plate actuator.

According to another aspect of the present invention, there is provided a power connecting / disconnecting device arranged in a power transmission system on a side of a wheel which is separated when a four-wheel drive vehicle is driven by two-wheel drive, and a clutch is connected by a gear plate type actuator of the present invention. Is in the four-wheel drive state, and the vehicle is in the two-wheel drive state when the clutch is disconnected.

Further, the power connection / disconnection device according to claim 4 uses the gear plate type actuator according to claims 1 to 3, so that a sufficient movement operation stroke with respect to the operated device is achieved as in the structure according to claims 1 to 3. In addition to being compact in the axial direction, advantages such as simple structure, light weight, low cost, and improved reliability can be obtained.

A differential device according to a fifth aspect of the present invention is an outer differential case which is rotated by receiving a driving force of a prime mover, an inner differential case which is relatively rotatably arranged inside the outer differential case, and a differential which is connected to the inner differential case. A gear plate actuator, comprising: a mechanism; a clutch for connecting and disconnecting the outer differential case and the inner differential case; and a gear plate actuator described in any one of claims 1 to 3, wherein the clutch is an operated device. It is characterized in that torque is interrupted between the outer differential case and the inner differential case by operating the clutch by a formula actuator.

According to a fifth aspect of the present invention, the differential device is a differential device that intermittently drives the driving force on the input side of the differential mechanism, and is arranged in a power transmission system on the wheel side that is disconnected during two-wheel drive of a four-wheel drive vehicle. If the clutch is connected by the gear plate type actuator of the present invention, the vehicle is
When the vehicle is in the wheel drive state and the clutch is disengaged, the vehicle is in the two wheel drive state.

The differential device according to claim 5 uses the gear plate type actuator according to any one of claims 1 to 3, so that a sufficient movement operation stroke with respect to the operated device can be achieved similarly to the configuration according to claims 1 to 3. In addition to being compact in the axial direction, it is possible to obtain effects such as a simple structure, lightweight, low cost, and improved reliability.

According to a sixth aspect of the present invention, in the differential device, any one of a differential case that rotates by receiving a driving force of a prime mover, a differential mechanism that distributes the rotation of the differential case from a pair of output side gears to a wheel side, and the output side gears. A clutch arranged between one of the wheels and the wheel thereof;
3. A gear plate type actuator having the clutch as an operated device according to claim 3, wherein torque is intermittently provided between the side gear and a wheel by operating the clutch by the gear plate type actuator. I am trying.

Further, the differential device according to claim 6 is a differential device which intermittently drives the driving force on the output side of the differential mechanism, and like the differential device according to claim 5, when a four-wheel drive vehicle drives two wheels. It is arranged in the power transmission system on the wheel side to be disconnected, and if the clutch is connected by the gear plate type actuator of the present invention, the vehicle becomes a four-wheel drive state, and if the clutch is released, the differential rotation of the differential mechanism is performed. The driving force is cut off and the vehicle enters the two-wheel drive state.

The differential device according to claim 6 uses the gear plate type actuator according to any one of claims 1 to 3, so that a sufficient movement operation stroke with respect to the operated device can be achieved similarly to the structure according to any one of claims 1 to 3. In addition to being compact in the axial direction, it is possible to obtain effects such as a simple structure, lightweight, low cost, and improved reliability.

According to a seventh aspect of the present invention, there is provided a differential device including a differential case which is rotated by a driving force of a prime mover, a differential mechanism which distributes the rotation of the differential case to a wheel side from a pair of output side gears, the differential case and the output side. A clutch that is arranged between any two of the side gears and limits a differential of the differential mechanism; and a gear plate type actuator according to any one of claims 1 to 3, wherein the clutch is an operated device. And limiting the differential of the differential mechanism by operating the clutch by the gear plate actuator.

In the differential device according to the seventh aspect, the differential of the differential mechanism is limited when the clutch is connected by the gear plate actuator of the present invention, and the differential is free when the clutch is disconnected.

Further, the differential device according to claim 7 uses the gear plate type actuator according to claims 1 to 3, so that a sufficient movement operation stroke with respect to the operated device can be achieved similarly to the structure according to claims 1 to 3. In addition to being compact in the axial direction, it is possible to obtain effects such as a simple structure, lightweight, low cost, and improved reliability.

[0044]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A gear plate actuator 1 according to an embodiment of the present invention and a rear differential 3 (differential device) using the same will be described with reference to FIGS.

FIG. 1 shows the rear differential 3, and the left and right directions are the left and right directions in a four-wheel drive vehicle in which the rear differential 3 is used. Further, members and the like not given reference numerals in the following description are not shown.

The rear diff 3 (differential device for distributing the driving force of the engine to the left and right rear wheels) is a differential device having an input / output function of the differential mechanism, and is used for a four-wheel drive vehicle. When driving two wheels, the drive force to the rear wheels is cut off.

The power transmission system of a four-wheel drive vehicle using the rear differential 3 includes an engine (motor), a transmission,
Transfer, 2-4 switching mechanism, front diff (differential device that distributes engine driving force to left and right front wheels), front axle, left and right front wheels, rear wheel propeller shaft, rear diff 3, rear axle, left and right rear wheels Etc.

The 2-4 switching mechanism constitutes a rear wheel output interface of the transfer, and as described below, it is operated to disconnect and connect simultaneously with the rear differential 3 to intermittently drive the rear wheel. .

The driving force of the engine is transmitted from the transmission to the transfer and distributed from the transfer to the front wheel side and the rear wheel side.

The driving force distributed to the front wheels is distributed from the front differential to the left and right front wheels via the front axle.

Further, the driving force distributed to the rear wheels is 2-
4 While the 4 switching mechanism and the rear differential 3 are connected,
4 switching mechanism and rear wheel side propeller shaft to rear differential 3
Is transmitted to the left and right rear wheels from the rear differential 3 via the rear axle, and the vehicle is in the four-wheel drive state.

When the connection between the 2-4 switching mechanism and the rear differential 3 is released, the rear wheel side is disconnected from the engine and the vehicle is in the two-wheel drive state.

The rear differential 3 is arranged inside the differential carrier 5, and an oil reservoir is formed inside the differential carrier 5.

The rear differential 3 includes a gear plate type actuator 1, an outer differential case 7, an inner differential case 9, a bevel gear type differential mechanism 11, and a dog clutch 13.
(Device to be operated: clutch) and the like.

Further, the gear plate type actuator 1
Is a support plate 15, a cam plate 17, a movable plate 19, a cam 21 (cam mechanism), a return spring 2.
3, shift spring 25, electric motor 27, gear set 2
9. It is composed of a controller and the like.

The rear differential 3 has a double casing structure composed of an outer differential case 7 and an inner differential case 9, and the inner differential case 9 is rotatably supported on the inner periphery of the outer differential case 7. Further, the left and right boss portions 31 and 33 formed on the outer differential case 7 are respectively provided with thrust bearings 35 to the differential carrier 5
Is supported by.

Bearing caps 37, 37 are screwed to the diff carrier 5 by screw parts 39. By rotating these bearing caps 37 by the screw parts 39, the outer race 41 is moved in the axial direction and the thrusts are thrust. The preload adjustment of the bearing 35 is performed.

The outer differential case 7 has a ring gear 43.
Are fixed with bolts 45. The ring gear 43 meshes with the drive pinion gear 47, and the drive pinion gear 47 is formed integrally with the drive pinion shaft 49. The drive pinion shaft 49 is connected to a transfer 2-4 switching mechanism via a joint and a rear wheel side propeller shaft, and the driving force of the engine is transferred from the transfer and 2-4 switching mechanism to the rear wheel side power transmission system. The outer differential case 7 is rotated via.

A clutch ring 51 is arranged inside the outer differential case 7, and is supported by the inner periphery of the outer differential case 7 so as to be movable in the axial direction.

The dog clutch 13 is composed of meshing teeth 53 and meshing teeth 55.
3 is formed on the left end of the clutch ring 51, and the meshing tooth 55 is formed on the right end of the inner differential case 9.

Further, openings 57 and 59 through which oil flows in and out are provided on the left and right of the outer differential case 7 at equal intervals in the circumferential direction. At the right end of the clutch ring 51, four leg portions 61 are provided at equal intervals in the circumferential direction, and these leg portions 61 engage with the right opening 59 and project to the outside.

The clutch ring 51 is moved left and right by the gear plate type actuator 1 as described below. When the clutch ring 51 is operated to move to the left, the dog clutch 13 meshes and the outer differential case 7 and the inner differential case 9 are connected, and the clutch ring 51 returns to the right, as in the lower half of FIG. , Figure 1
As shown in the upper half of the figure, the dog clutch 13 is disengaged, and the outer differential case 7 and the inner differential case 9 are released.
And are separated.

A thrust washer 63 which receives an operating force from the gear plate type actuator 1 is arranged between the left end portion of the inner differential case 9 and the outer differential case 7, and the inner differential case 9 has the thrust washer 63 interposed therebetween. It is positioned to the left in the axial direction.

The bevel gear type differential mechanism 11 is composed of a plurality of pinion shafts 65, a pinion gear 67, left and right output side gears 69, 71 and the like.

The tip of each pinion shaft 65 has through holes 73 formed in the inner differential case 9 at equal intervals in the circumferential direction.
, And is prevented from coming off by a spring pin 75.

The pinion gears 67 are rotatably supported on the respective pinion shafts 65, and the side gears 69,
71 is meshed with each pinion gear 67 from the left and right.

The boss portions 77, 7 of the side gears 69, 71
Reference numeral 9 denotes bearing portions 81 and 8 formed on the outer differential case 7.
3, the left and right rear axles are splined to the bosses 77 and 79, respectively.

Further, thrust washers 85 are arranged between the side gears 69, 71 and the outer differential case 7, respectively, and receive the thrust force of meshing between the side gears 69, 71.

A spherical washer portion 87 is formed on the inner circumference of the inner differential case 9 so as to face the back surface of each pinion gear 67. The centrifugal force of the pinion gear 67 and the meshing of the side gears 69 and 71 allow the pinion gear 67 to mesh with each other. Gear 67
Bears the meshing reaction force that he receives.

The support plate 15 of the gear plate type actuator 1 is pressed, and as shown in FIGS. 2, 3 and 8, an annular plate portion 89 and two fixed plate portions integrally formed with the annular plate portion 89. 91, three assembly recesses 93 provided on the inner circumference of the annular plate portion 89 at equal intervals in the circumferential direction, and the annular plate portion 89.
Two guide grooves 95 provided at equal intervals in the circumferential direction on the outer periphery of the
Etc.

The cam plates 17 are pressed, and as shown in FIGS. 4, 5 and 8, the annular plate portion 97, the gear plate 99, and the three inner plate portions 97 provided at equal intervals in the circumferential direction. Assembly recesses 101, three support projections 103 provided adjacent to each recess 101 in the circumferential direction, and annular plate 9
It is composed of three cam pieces 105 and the like which are provided along the inner circumference of 7 at equal intervals in the circumferential direction.

As shown in FIG. 16, each cam piece 105 is provided radially inside each support projection 103.

The gear plate 99 is formed integrally with the annular plate portion 97, and the gear 107 is provided on the outer periphery thereof. The support protrusion 103 is composed of an axial portion 109 formed on the annular plate portion 97 and a radial portion 111 formed at the end of the axial portion 109.

Each cam piece 105 is shown in FIGS.
5, it is composed of an inclined surface 113 (cam surface), a holding surface 115 formed without a cam angle in the radial direction, and a holding projection 117 formed between the inclined surface 113 and the holding surface 115. .

The movable plate 19 is pressed, and as shown in FIGS. 6, 7 and 8, the annular plate portion 119 (base portion),
Three cam guide pieces 121 (protrusions) provided on the inner circumference of the annular plate portion 119 at equal intervals in the circumferential direction, and each cam guide piece 121.
It is composed of three inner peripheral guide pieces 123 provided between the two, and two outer peripheral guide pieces 125 provided on the outer periphery of the annular plate portion 119 at equal intervals in the circumferential direction.

Further, each cam guide piece 121 includes an axial portion 127 formed on the annular plate portion 119 and an axial portion 1.
It is composed of a radial portion 129 formed at the end of 27.

The support plate 15, the cam plate 17, and the movable plate 19 are assembled as shown in FIG. 9, and this assembly is performed in the following order.

First, each support projection 10 of the cam plate 17
3 from the right side to the respective mounting recesses 93 of the support plate 15.
After inserting the cam plate 17 in the direction shown by the arrow 131 in FIG. 8 until the assembling recesses 101 of the cam plate 17 overlap with the assembling recesses 93 of the support plate 15, as shown in FIG. The radial portion 111 of each support projection 103 of the cam plate 17 surrounds and engages with the inner peripheral end of the annular plate portion 89 of the support plate 15, and in this state, each cam piece 105 of each cam plate 17 (each cam 21) is located radially inside the support plate 15.

Then, the cam guide pieces 121 of the movable plate 19 are inserted from the left side into the mounting recesses 93 and 101 of the support plate 15 and the cam plate 17, and then the cam plate 17 is moved in the direction of arrow 133 in FIG. When the movable plate 19 is rotated to the right, the movable plate 19 is moved by the radial portion 129 of each cam guide piece 121 to form the annular plate portion 97 of the cam plate 17.
Engage with.

In this way, each plate 15, 17, 19
Assembly is extremely easy because there are few steps.

With the assembly completed, the support plate 1
5 and the annular plate portions 89 and 97 of the cam plate 17 are guided on the inner periphery by the inner peripheral guide pieces 123 of the movable plate 19, and thus the support plate 15, the cam plate 17 and the movable plate 19 are centered with respect to each other. There is. Further, the cam plate 17 is rotatable with respect to the support plate 15 and the movable plate 19.

As shown in FIG. 1, each fixing plate portion 91 of the support plate 15 is fixed to the diff carrier 5 together with the mounting bracket 135 of the electric motor 27 by the bolt 137.

As shown in FIGS. 11, 13 and 15, the cam 21 is composed of each cam piece 105 of the cam plate 17 and each cam guide piece 121 (radial portion 129) of the movable plate 19.

The return spring 23 is integrally formed with the retainer 139 of the clutch ring 51 as shown in FIG. As shown in FIGS. 1, 8 and 9, this retainer 139
The arm portion 141 formed in the above is fixed to each leg portion 61 of the clutch ring 51, and the ring 143 is arranged between the retainer 139 (return spring 23) and the right end portion of the outer differential case 7.

The clutch ring 51 and the retainer 139 can integrally move back and forth in the axial direction, and the return spring 23 urges the clutch ring 51 in the disengagement direction (to the right) of the dog clutch 13.

The shift spring 25, as shown in FIG.
It is formed integrally with the movable plate 19. The urging force of the shift spring 25 is made larger than the urging force of the return spring 23, so that the movable plate 19 and the clutch ring 51 are engaged with each other in the dog clutch 13 (leftward direction).
Is urged to.

The return spring 23 and the shift spring 25 may be a coil spring 145 and a coil spring 147, respectively, as shown in FIG.

Further, the cam plate 17 is provided with three spring seats 149 for the coil springs 147 at equal intervals in the circumferential direction.

The electric motor 27 is fixed to the differential carrier 5 via a mounting member 135. Electric motor 2
7 is rotatable in both directions, and is connected to a vehicle-mounted battery via a controller.

The gear set 29 is the output shaft 1 of the electric motor 27.
The pinion gear 153 fixed to 51 and the gear 107 of the cam plate 17 (gear plate 99) are configured to amplify the rotational torque of the electric motor 27 and rotate the cam plate 17.

The controller performs the intermittent operation of the dog clutch 13 in the following manner, and when switching from the two-wheel drive state to the four-wheel drive state, the controller simultaneously operates the dog clutch 13 and the 2-4 switching mechanism, When switching from the four-wheel drive state to the two-wheel drive state, they are simultaneously decoupled.

When the dog clutch 13 is engaged or disengaged, the controller performs time control for rotating the electric motor 27 in both directions (direction opposite to one direction) for a predetermined time (angle). When the electric motor 27 rotates for a predetermined time, the cam plate 17 is rotated through a gear set 29 in a predetermined direction by a predetermined angle.

FIG. 10 shows a state in which the gear plate 99 is rotated in one direction by the maximum angle, and the pinion gear 153 of the gear set 29 is meshed with one end of the gear 107. At this time, one fixed plate portion 91 of the support plate 15 abuts against the gear plate 99 and functions as a stopper, which prevents the cam plate 17 from excessively rotating and prevents the gear 107 from coming off the pinion gear 153.

FIG. 11 shows the state of the cam 21 corresponding to FIG. 10, and the radial portion 129 of each cam guide piece 121 (movable plate 19) is the inclined surface 113 of each cam piece 105 (cam plate 17). Before going up, the radial portion 129 is pressed against the annular plate portion 97 by the urging force of the shift spring 25, and the cam 21 is not operating. Further, each arrow in FIGS. 10 and 11 indicates the moving direction of the cam plate 17 and the cam guide piece 121 (movable plate 19) when the electric motor 27 is rotated in the opposite direction from each state.

When the cam 21 is not in operation, as shown in FIG.
The movable plate 19 (clutch ring 51) is moved to the left by the shift spring 25 as in the lower half of
The dog clutch 13 is engaged.

At this time, the shift spring 25 serves as a waiting mechanism and engages the dog clutch 13 when the meshing teeth 53 and 55 are in phase with each other.

When the dog clutch 13 is engaged, the vehicle enters the four-wheel drive state as described above.

FIG. 12 shows the electric motor 2 from the state of FIG.
7 shows a state in which 7 is rotated by the maximum angle in the opposite direction,
The pinion gear 153 of the gear set 29 meshes with the other end of the gear 107. At this time, the other fixed plate portion 91 of the support plate 15 abuts against the gear plate 99 and serves as a stopper, preventing the cam plate 17 from over-rotating and preventing the gear 107 from coming off the pinion gear 153.

FIG. 13 shows the state of the cam 21 corresponding to FIG. 12, and shows the radial portion 1 of each cam guide piece 121.
29 goes up the inclined surface 113 of each cam piece 105, goes over the holding projection 117, and is held by the holding surface 115.
Is operating. 12 and 13 show the moving directions of the cam plate 17 and the cam guide piece 121 (movable plate 19) when the electric motor 27 is rotated in the opposite direction from the respective states.

When the cam 21 operates, each cam guide piece 121 (movable plate 19) is driven by the cam thrust force.
Moves upward in FIG. 13 and presses the shift spring 25.

When the shift spring 25 is contracted, the movable plate 19 (clutch ring 51) is moved to the right by the urging force of the return spring 23, and the dog clutch 13 is disengaged, as in the upper half of FIG. To be done.

When the dog clutch 13 is disengaged, the vehicle enters the two-wheel drive state as described above.

Further, since the holding projection 117 holds each cam guide piece 121 on the holding surface 115 by its check function, it receives a disturbance factor such as vibration or impact while traveling while the electric motor 27 is stopped. However, it is possible to prevent the vehicle from changing from the two-wheel drive state to the four-wheel drive state against the driver's intention.

FIG. 14 shows a state in which the pinion gear 153 meshes with the central portion of the gear 107 while the cam plate 17 is being rotated in both directions from the states shown in FIGS. 10 and 12, and FIG. At this time, the moving direction (arrow 157) of each cam guide piece 121 (movable plate 19) according to the rotating direction (arrow 155) of the cam plate 17 is shown.

When the cam plate 17 is rotated in the direction of arrow 159 in FIG. 14, it becomes the four-wheel drive state in FIG. 10, and when it is rotated in the direction of arrow 161, it becomes the two-wheel drive state in FIG.

Further, the holding surfaces (the holding surface 115 and the annular plate portion 9) having no cam angle are provided on both sides of the inclined surface 113 of the cam piece 105.
7) is provided, when the cam guide piece 121 (radial portion 129) rides on these holding surfaces,
Even if the biasing force of the shift spring 25 is received, the rotational torque is not applied to the cam plate 17. Therefore, the state of the cam 21 is maintained both before and after the operation, and the vehicle is
Since the wheel drive state and the two-wheel drive state are stably maintained, the electric motor 27 can be stopped except when the cam 21 is operated.

As described above, the dog clutches 13 and 2-
In a four-wheel drive state in which four switching mechanisms are connected,
The driving force of the engine is transmitted from the 2-4 switching mechanism to the outer differential case 7 via the rear wheel side power transmission system, and the inner differential case 9 is rotationally driven via the dog clutch 13. This rotation is distributed from the pinion shaft 65 to the side gears 69 and 71 via the pinion gear 67 and transmitted to the left and right rear wheels via the respective axles.

When the vehicle is in the four-wheel drive state, the running performance, the escape performance and the stability on a bad road are improved.

Further, for example, when a driving resistance difference occurs between the rear wheels during traveling on a rough road, the driving force of the engine is differentially distributed to the left and right rear wheels by the rotation of each pinion gear 67.

In the two-wheel drive state in which the connection between the dog clutch 13 and the 2-4 switching mechanism is released, the inner differential case 9 to the rear wheels are disengaged by the dog clutch 13 to be in the free rotation state and 2-4. The power transmission system from the switching mechanism to the outer differential case 7 is separated from both the driving force of the engine and the accompanying rotation of the rear wheels, and the rotation is stopped.

As described above, in the two-wheel drive state in which the rotation of the rear wheel power transmission system from the 2-4 switching mechanism to the outer differential case 7 is stopped, the vibration is reduced, the riding comfort is improved, and the rear wheel power is reduced. Wear is reduced in each part of the transmission system to improve durability, and further, the load on the engine is reduced by the reduction of the rotational resistance, and fuel consumption is improved.

The outer differential case 7 has openings 57, 5
9, spiral oil grooves 163 and 165 are formed on the inner circumferences of the boss portions 31 and 33, respectively. Further, oil grooves 163 and 165 are formed on the portions facing the thrust washers 85 and 85, respectively. The communicating oil grooves 167 and 169 in the radial direction are formed.

Since the openings 57 and 59 are formed in the radially outer portion of the outer differential case 7, the differential carrier 5
Is constantly immersed in the oil in the oil pool formed in
As the outer differential case 7 rotates, oil flows in and out through the openings 57 and 59.

The oil in the oil sump is scraped up by the rotation of the outer differential case 7 (ring gear 43), and the scraped oil is promoted to move by the screw pump action of the oil grooves 163 and 165, so that the oil groove 16
7, 169 and the thrust washers 85, 85 and the like to flow into the outer differential case 7.

The oil that has flowed into the outer differential case 7 meshes with the gears 67, 69, 71 that constitute the differential mechanism 11, the pinion shaft 65 and the pinion gear 67.
Sliding part, outer differential case 7 and inner differential case 9, sliding part, outer differential case 7 and clutch ring 5
1 sliding portion, dog clutch 13 (interlocking teeth 53, 5
5) is supplied to lubricate and cool them.

The lower part of the gear plate type actuator 1 is also immersed in the oil sump, and the cam plate 17, the support plate 15 and the movable plate 19 which are rotated are operated.
The sliding parts, the cam 21, and the like are also lubricated and cooled.

The gear set 29 is also lubricated and cooled by the scraping oil.

In each of the above-mentioned lubrication / cooling sections, the oil supplied reduces wear and improves durability, reduces frictional resistance at each sliding section, and improves fuel efficiency of the engine.

As shown in FIG. 16, each cam piece 105 (cam 21) of the cam plate 17 is provided on the inside of each support projection 103 in the radial direction, so that each cam piece 105 and each support projection 1
Since 03 and 03 do not overlap in the axial direction, the cam plate 17 is formed thinner in the axial direction.

Further, with the plates 15, 17, and 19 assembled, the support plate 15 and the cam plate 17 are arranged inside the annular plate portion 119 of the movable plate 19 and the radial portion 129 in the axial direction (in the axial portion 127). The cam 21 is disposed on the inner side of the support plate 15, and the cam 21 is disposed on the inner side of the support plate 15 in the radial direction.
Since the cam plate 17 is formed thin in the axial direction as described above, the axial dimension W of the movable plate 19 (the outer dimension of the annular plate portion 119 and the radial portion 129: the axial portion 127) is reduced, Each plate 15, 17,
Nineteen assemblies are axially compact.

Thus, the gear plate type actuator 1 and the rear differential 3 are constituted.

In the gear plate type actuator 1, as described above, the cam 21 is provided on the radially inner side of the support plate 15, and the cam piece 105 is provided on the radially inner side of the support projection 103, so that the cam plate 17 is axially arranged. By making it thinner, the axial dimension W of the movable plate 19 becomes smaller, and the assembly of the plates 15, 17, and 19 is made compact in the axial direction.

Therefore, since the stroke of the movable plate 19 can be increased by that much, the clutch ring 51 of the dog clutch 13, which requires a large operation stroke, can be moved by a sufficient stroke amount for intermittent operation. .

Further, while the sufficient stroke amount is obtained in this way, the gear plate type actuator 1 and the rear differential 3 are
Can be made compact in the axial direction, and the vehicle mountability of the rear differential 3 can be improved.

The gear plate type actuator 1 for converting the rotational torque of the electric motor 27 into the operating force of the dog clutch 13 by the cam 21 is different from the conventional example using the fluid pressure type actuator in that an expensive pump and piston are used. Cylinder, shift mechanism etc. are unnecessary,
The number of parts is small, the structure is simple, and the cost is low.

Further, the gear plate type actuator 1
The rear diff 3 using is not required to have a wide space for arranging pressure lines and the like, and is lightweight and compact to improve the vehicle mountability. Further, it is not necessary to change the diff carrier 5, and a large cost increase is caused by the change. Is prevented.

Further, the gear plate type actuator 1 and the rear differential 3 are released from the influence of the function deterioration and the pressure fluctuation due to the pressure leakage, and the performance, stability and reliability are greatly improved, and the seal of each part of the pressure line is improved. It is also possible to avoid strengthening and the resulting increase in costs.

In the gear plate type actuator of the present invention, the operated device is not limited to the clutch.

The clutch is not limited to the meshing clutch (dog clutch) as in the above embodiment,
A friction clutch such as a multi-plate clutch or a cone clutch may be used.

In this case as well, by making the support plate, the cam plate, the movable plate and the cam mechanism axially compact, the power interruption device and the differential device using the gear plate type actuator can be made compact to improve the vehicle mountability. You can

In the differential device of the present invention, the differential mechanism is not limited to the bevel gear type differential mechanism,
A planetary gear type differential mechanism, a differential mechanism in which a side gear on the output side is connected by a pinion gear rotatably accommodated in an accommodation hole of a differential case, a differential mechanism using a worm gear, and the like may be used.

[0132]

According to the gear plate type actuator of the first aspect of the present invention, since the cam mechanism is provided radially inward of the support plate, the cam mechanism and each plate are thinned in the axial direction. While being sufficiently large, the gear plate actuator and the device using the same can be made compact in the axial direction and the vehicle mountability can be improved.

In the gear plate type actuator of the second aspect, the same effect as that of the first aspect can be obtained by making the movable plate thinner in the axial direction.

In the gear plate type actuator of the third aspect, the cam plate is thin in the axial direction, so that the same effect as that of the first or second aspect can be obtained.

The power connecting / disconnecting device of the fourth aspect is the first to third aspects.
By using the gear plate type actuator of
It has a large operation stroke, is compact in the axial direction, and has the advantages of simple structure, lightweight, low cost, and improved reliability.

The differential device of claim 5 uses the gear plate type actuator of claims 1 to 3 to obtain a large operation stroke, is compact in the axial direction, and has a simple structure, light weight, and low cost. It is possible to obtain effects such as improvement in reliability.

The differential device according to claim 6 uses the gear plate type actuator according to claims 1 to 3 to obtain a large operation stroke, is compact in the axial direction, and has a simple structure, light weight, and low cost. It is possible to obtain effects such as improvement in reliability.

The differential device according to claim 7 uses the gear plate type actuator according to claims 1 to 3 to obtain a large operation stroke, is compact in the axial direction, and has a simple structure, light weight, and low cost. It is possible to obtain effects such as improvement in reliability.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a gear plate type actuator of one embodiment and a rear differential using the same.

FIG. 2 is a front view of a support plate used in the embodiment of FIG.

3 is a cross-sectional view taken along the line AA of FIG.

FIG. 4 is a front view of a cam plate used in the embodiment of FIG.

5 is a sectional view taken along line BB of FIG.

FIG. 6 is a front view of a movable plate used in the embodiment of FIG.

FIG. 7 is a sectional view taken along line CC of FIG.

8 is an exploded perspective view showing a support plate, a cam plate, a movable plate and the like used in the embodiment of FIG.

9 is a perspective view showing a state where each member of FIG. 8 is sub-assembled.

FIG. 10 is a front view showing the angle of the cam plate when the vehicle is in the four-wheel drive state.

11 is a drawing showing the state of the cam when the cam plate is at the angle of FIG. 10. FIG.

FIG. 12 is a front view showing the angle of the cam plate when the vehicle is in the two-wheel drive state.

FIG. 13 is a view showing a state of the cam when the cam plate is at the angle shown in FIG. 12;

FIG. 14 is a front view showing an angle of a cam plate when the vehicle is switched between a four-wheel drive state and a two-wheel drive state.

FIG. 15 is a view showing a state of the cam when the cam plate is at the angle shown in FIG. 14;

16 is a cross-sectional view of main parts of the embodiment of FIG.

FIG. 17 is a sectional view of a conventional example.

[Explanation of symbols]

1 Gear Plate Actuator 3 Rear Differential (Differential Device) 7 Outer Differential Case 9 Inner Differential Case 11 Bevel Gear Type Differential Mechanism 13 Dog Clutch (Operated Device: Clutch) 15 Support Plate 17 Cam Plate 19 Movable Plate 21 Cam (Cam Mechanism) 25 Shift spring 27 Electric motor 29 Gear set 99 Gear plate 103 Support protrusion 105 Cam piece of cam plate (cam mechanism provided on the radial inside of the support plate) 113 Inclined surface (cam surface) of cam piece 119 Annular plate of movable plate Part (base) 121 Cam guide piece (projection) of movable plate 127 Axial portion of cam guide piece 129 Radial portion of cam guide piece

   ─────────────────────────────────────────────────── ─── Continued front page    F term (reference) 3D036 GA14 GA38 GB05 GD02 GD06                       GD09 GF06 GF10 GH05 GH12                       GJ17                 3D043 AA06 AA10 AB01 AB17 EA02                       EA17 EB03 EB12                 3J027 FA17 FA34 FA37 FB02 HA01                       HB07 HC23 HC26 HD01 HE04                       HF05 HG07 HH13

Claims (7)

[Claims] 1. An annular support plate fixed to a stationary side, a cam plate rotatably mounted on one side of the support plate in the axial direction so as to be rotatable in the forward and reverse directions, and an axial direction to the other side of the support plate in the axial direction. A movable plate that is movably arranged to move and operate the operated device, a gear set including a gear provided on the gear plate on the cam plate side, and the cam plate via the gear set. A cam mechanism that is provided between the cam plate and the movable plate and that converts a rotational force of the cam plate into a moving operation force of the movable plate. A gear plate type actuator, wherein a mechanism is provided inside the support plate in a radial direction. 2. The invention according to claim 1, wherein the movable plate includes an axial portion formed at a radial end portion of a base portion and a radial portion formed at the axial portion. Is provided, the support plate and the cam plate are arranged axially inward of the base portion and the radial portion of the movable plate, and the cam mechanism is the radial portion of the movable plate. And a cam surface provided on the cam plate and in contact with the radial portion, the gear plate actuator. 3. The invention according to claim 1, wherein the cam plate is provided with a support protrusion that surrounds and supports an inner peripheral end portion of the support plate. Is provided on the radially inner side of the support protrusion. 4. A pair of torque transmission members, a clutch arranged between the torque transmission members, and a gear plate type actuator according to claim 1, wherein the clutch is an operated device. And a torque interrupting device between the torque transmitting members when the clutch is operated by the gear plate actuator. 5. An outer differential case that rotates by receiving a driving force of a prime mover, an inner differential case that is relatively rotatably arranged inside the outer differential case, a differential mechanism connected to the inner differential case, and the outer differential case. And a clutch that connects and disconnects the inner differential case with the inner differential case, and a gear plate type actuator according to any one of claims 1 to 3, wherein the clutch serves as an operated device. A differential device characterized in that a torque is interrupted between the outer differential case and the inner differential case by an operation. 6. A differential case that rotates by receiving the driving force of a prime mover, a differential mechanism that distributes the rotation of the differential case from a pair of output side gears to a wheel side, and one of the output side gears and its wheels. And a gear plate actuator having the clutch as an operated device according to any one of claims 1 to 3, wherein the side gear is operated by operating the clutch with the gear plate actuator. A differential device characterized by intermittent torque between a wheel and a wheel. 7. A differential case that rotates by receiving the driving force of a prime mover, a differential mechanism that distributes the rotation of the differential case from a pair of output side gears to a wheel side, and any two of the differential case and the output side gears. A gear plate actuator that is arranged between the clutch and that limits the differential of the differential mechanism; and a gear plate actuator that uses the clutch as an operated device according to claim 1. A differential device characterized in that the differential of the differential mechanism is limited by the operation of the clutch by a rotary actuator.