JP2003294113A - Fixing structure for gear plate type actuator to differential carrier, power disconnecting device using the same gear plate type actuator, and differential device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To facilitate assembling and positioning to an operated device, and to achieve simple structure and low cost. <P>SOLUTION: A gear plate actuator is provided with a support plate 15, a cam plate, and a movable plate assembled with each other, a differential carrier 5 to support the plate 15, an electric motor to operate the cam plate to be rotated, and a cam mechanism to covert rotation of the cam plate into moving operation force to the movable plate. A fixing slit 175 is provided in the differential carrier 5. A support plate 91 is provided on the plate 15. The support part 91 is engaged with the fixing slit 175 to fix and position the plate 15 to the differential carrier 5. <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 structure for fixing a gear plate type actuator for operating an operated device such as a clutch to a differential carrier, a power connection / disconnection device for connecting / disconnecting a driving force by this clutch, and a drive for this clutch. The present invention relates to a differential device that interrupts force or limits 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 disconnected from the engine side, the vehicle is in the two-wheel drive state, and the fuel consumption of the engine is improved.

Further, in addition to a fluid pressure type actuator such as a pneumatic actuator used in the differential device 1001, a cam mechanism formed between the plates is operated by a rotating torque of an electric motor to operate an operated device such as a clutch. There is an actuator that converts to.

[0010]

As described above, in the case of the actuator in which the cam mechanism between the plates is driven by the electric motor, the plates are conventionally bolted to the stationary casing (differential carrier).

Therefore, in addition to the bolts, it is necessary to form screw holes for the bolts on the differential carrier, a seat for the bolts is required on the plate, and it is necessary to form through holes for the bolts on this seat. Therefore, the number of parts is increased by the number of bolts and the cost is increased, the plate is increased in cost only by the seat for the bolt, and the processing cost of the differential carrier and the plate is increased only by the screw hole and the through hole for the bolt.

Further, in the case of bolting, the number of assembling steps is large, the assembling cost is high accordingly, and axial positioning and radial positioning of the plate are difficult.

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, and the performance thereof deteriorates and becomes unstable.

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, the present invention is extremely easy to assemble and position with respect to the operated device, and has a simple structure.
It is an object of the present invention to provide a low-cost and highly reliable structure for fixing a gear plate type actuator to a differential carrier, and a power interruption device and a differential device configured by using this gear plate type actuator.

[0019]

According to a first aspect of the present invention, there is provided an annular support plate fixed to a differential carrier, a cam plate disposed on one side of the support plate in the axial direction so as to be rotatable forward and backward, and A movable plate that is arranged axially movably on the other side of the support plate in the axial direction and that moves and operates the operated device; and a gear set that includes a gear provided on the gear plate on the cam plate side, An electric motor that rotates the cam plate in the forward and reverse directions via the gear set is provided between the cam plate and the movable plate, and the rotational force of the cam plate is used as the movement operation force of the movable plate. A structure for fixing a gear plate type actuator having a cam mechanism for converting to a diff carrier, wherein a fixing slit is provided on an inner wall of the diff carrier, and the supporting plate is provided. The support portion is provided, from engaging the support portion to the fixing slits, characterized in that fixed to said support plate to said differential carrier on.

In the structure for fixing the gear plate type actuator to the differential carrier according to the first aspect, the supporting plate can be assembled very easily by simply engaging the supporting portion of the supporting plate with the fixing slit on the side of the differential carrier. Is completed.

As described above, according to the present invention, since bolting is not used for the assembling, the number of assembling steps is extremely small and the assembling cost is greatly reduced.

Further, the number of parts and the cost are reduced by the number of bolts, and the supporting plate does not need a seat for bolts, so that the shape is simple and the cost is low, and the diff carrier does not require the processing of screw holes. Therefore, the support plate does not need to be processed for the bolt through hole, and the processing cost is reduced.

In addition to axial positioning by the fixing slits on the differential carrier side, radial positioning (centering) can be performed by the outer circumference of the operated device as described below.

Further, the gear plate type actuator of the present invention, which is configured to convert 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. No expensive pump, fluid pressure type actuator (piston and cylinder), shift mechanism, etc. are required, the number of parts is small, the structure is simple, and the cost can be reduced.

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 increased accordingly. Can be avoided.

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

Further, unlike the fluid pressure type actuator, since a wide arrangement space such as a pressure line and its routing space is not required, the gear plate type actuator and the operated device can be made light and compact and can be mounted on a vehicle. Is greatly improved.

According to a second aspect of the present invention, there is provided a structure for fixing the gear plate actuator according to the first aspect to the differential carrier, wherein the differential carrier has a first member and a second member, and the first member is a first member. The member is provided with the fixing slit, and after the supporting portion of the supporting plate is engaged with the fixing slit of the differential carrier, the second member is attached to the first member.
It is characterized in that the support plate is prevented from rotating by fixing it to a member, and it is possible to obtain the same operation and effect as the configuration of claim 1.

Further, due to the rotation preventing function of the second member,
The gear plate actuator has stable operation and improved durability.

According to a third aspect of the present invention, there is provided a structure for fixing the gear plate type actuator according to the first or second aspect to the differential carrier, wherein the fixing slit of the differential carrier and the supporting portion of the supporting plate are provided. The supporting plate is positioned in the radial direction with respect to the differential carrier by forming a wedge-shaped contact portion therebetween, and an operation and an advantage equivalent to those of the configuration according to claim 1 or 2 are obtained. be able to.

Since the wedge-shaped contact portion is provided between the fixing slit and the support portion, the support plate (support portion) is simply assembled (engaged) with the differential carrier (fixing slit) for radial positioning. (Centering) is performed.

As described above, since the diff carrier side fixing slit has a positioning function in the axial direction, the structure according to claim 3 is extremely excellent in both the axial direction and the radial direction only by assembling the support plate to the diff carrier. Positioning can be performed easily.

According to the second aspect of the present invention, since the wedge-shaped contact portions are pressed against each other by fixing the second member of the differential carrier to the first member, the radial positioning function is further ensured.

According to a fourth aspect of the present invention, there is provided a structure for fixing the gear plate type actuator according to any one of the first to third aspects to a differential carrier, wherein the support plate, the cam plate and the movable plate are Each of them is formed in a ring shape and is positioned in the radial direction on the outer circumference of the operated device, and it is possible to obtain the same actions and effects as the configurations of claims 1 to 3.

Further, in this construction in which the outer circumference of the operated device is used for radial positioning, it is not necessary to separately prepare a radial positioning mechanism, and radial positioning can be performed at extremely low cost.

According to a fifth aspect of the present invention, there is provided a power connection / disconnection device according to any one of the first to fourth aspects, wherein a pair of torque transmission members and a clutch disposed 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 two-wheel drive vehicle is driven in a four-wheel drive vehicle. Is in the four-wheel drive state, and the vehicle is in the two-wheel drive state when the clutch is disconnected.

According to a fifth aspect of the present invention, there is provided a power connection / disconnection device using the gear plate type actuator fixing structure according to any one of the first to fourth aspects.
Similar to the configurations of 4 to 4, the support plate can be assembled very easily, and the effects such as simple structure, light weight, low cost, and improved reliability can be obtained.

A differential device according to a sixth 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 disposed inside the outer differential case, and a differential which is connected to the inner differential case. The gear plate, comprising: a mechanism; a clutch for connecting and disconnecting the outer differential case and the inner differential case; and a gear plate actuator having the clutch as an operated device according to any one of claims 1 to 4. 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.

A differential device according to a sixth aspect of the present invention is a differential device in which a driving force is interrupted on the input side of a differential mechanism, and the differential device is arranged in a power transmission system on a wheel side which 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.

Further, the differential device according to claim 6 uses the structure for fixing the gear plate type actuator according to any one of claims 1 to 4 to the differential carrier, so that the differential device can be supported similarly to the structure according to any one of claims 1 to 4. The plate is extremely easy to assemble, and the effects such as simple structure, light weight, low cost, and improved reliability can be obtained.

In the differential device according to a seventh aspect of the present invention, 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;
4. A gear plate type actuator having the clutch as an operated device according to claim 4, wherein torque is intermittently provided between the side gear and the wheel by operating the clutch by the gear plate type actuator. I am trying.

Further, the differential device according to claim 7 is a differential device which intermittently drives the driving force at the output side of the differential mechanism. Like the differential device according to claim 6, the four-wheel drive vehicle is used for two-wheel drive. 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.

Further, the differential device according to claim 7 uses the structure for fixing the gear plate type actuator according to any one of claims 1 to 4 to the differential carrier, so that the differential device can be supported similarly to the structure according to any one of claims 1 to 4. The plate is extremely easy to assemble, and the effects such as simple structure, light weight, low cost, and improved reliability can be obtained.

According to another 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 arranged between any two of the side gears to limit the differential of the differential mechanism, and a gear plate type actuator according to any one of claims 1 to 4, wherein the clutch is an operated device. And limiting the differential of the differential mechanism by operating the clutch by the gear plate actuator.

Further, in the differential device according to the eighth aspect, the differential of the differential mechanism is limited if the clutch is connected by the gear plate type actuator of the present invention, and the differential becomes free if the clutch is disconnected.

Further, the differential device according to claim 8 uses the structure for fixing the gear plate type actuator according to any one of claims 1 to 4 to the differential carrier, so that the differential device can be supported similarly to the structure according to any one of claims 1 to 4. The plate is extremely easy to assemble, and the effects such as simple structure, light weight, low cost, and improved reliability can be obtained.

[0048]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A structure for fixing a gear plate actuator 1 to a differential carrier (one embodiment) and a rear differential 3 (a differential device of one embodiment) using the structure 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 a driving force interrupting function on the input side 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 in which the rear differential 3 is used is 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 side output interface, and is operated to release and connect the rear diff 3 simultaneously with the rear differential 3, as described below, to interrupt the driving force to the rear wheel side. .

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 actuator 1, an outer differential case 7, an inner differential case 9, a bevel gear 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 slidably 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 each thrust is moved. 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 is provided with the thrust washer 63 via the thrust washer 63. 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 periphery 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 side gears 69 and 71 mesh with each other to form a pinion gear. Gear 67
Bears the meshing reaction force that he receives.

The support plate 15 of the gear plate type actuator 1 is press-worked, as shown in FIGS.
7, an annular plate portion 89, two fixed plate portions 91 (supporting portions) integrally formed with the annular plate portion 89, and three fixed plate portions 89 provided on the inner periphery of the annular plate portion 89 at equal intervals in the circumferential direction. Assembly recess 9
3 (support plate side insertion hole), and two guide grooves 95 provided at equal intervals in the circumferential direction on the outer periphery of the annular plate portion 89.

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 annular plate portions 97 provided on the inner periphery of the annular plate portion 97 at equal intervals in the circumferential direction. Assembly recesses 101 (cam plate side insertion holes), three support protrusions 103 (cam plate side protrusions) provided adjacent to each recess 101 in the circumferential direction, and annular plate portion 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.

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, the inclined surface 113, the holding surface 115 having no cam angle formed in the radial direction, the inclined surface 113 and the holding surface 115.
It is composed of a holding protrusion 117 formed between and.

The movable plate 19 is pressed, and as shown in FIGS. 6, 7 and 8, an annular plate portion 119 and three cam guide pieces provided on the inner periphery of the annular plate portion 119 at equal intervals in the circumferential direction. 121 (movable plate side protrusion), three inner peripheral guide pieces 123 provided between the cam guide pieces 121, 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. Etc.

Further, each cam guide piece 121 has 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.
Then, the cam plate 17 is rotated in the direction of 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, respectively. Plate 17
Engage with the annular plate portion 89 of the support plate 15 by the radial portion 111 of each support protrusion 103.

Next, the cam guide pieces 121 of the movable plate 19 are inserted from the left into the mounting recesses 93, 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. 17, the differential carrier 5 is divided into a casing member 171 (first member) and a cover 173 (second member).

As shown in FIG. 16, the casing member 171 is provided with fixing slits 175 and 175 with which the fixing plate portions 91 of the support plate 15 are engaged. Also, FIG.
7, wedge-shaped contact portions 177 and 177 are formed between the fixing slits 175 and 175 and the fixing plate portions 91 and 91.

After the cam plate 17 and the movable plate 19 are assembled as described above, as shown in FIG. 17, the support plate 15 has the fixing plate portions 91, 91 fixed to the fixing slit 17.
5, 175 respectively, and then the cover 173
Are bolted to the casing member 171.

Each of the plates 15, 17, 19 has the support plate 15 (fixed plate portions 91, 91) as the casing member 17.
1 (fixing slits 175, 175), the fixing slits 175, 175 are axially formed.
The fixing slits 175 and 175 having a wedge shape and the fixing plate portion 91, which are positioned in the radial direction.
It is positioned by the contact portions 177 and 177 of 91.

Further, the cover 173 is the casing member 1
In the state of being fixed to 71, the fixing plate portions 91, 91 and the contact portions 177, 177 are appropriately pressed to support the support plate 15
While confirming radial positioning (centering) of (each plate 15, 17, 19), rotation is stopped.

As described above, by simply engaging the fixing plate portions 91, 91 with the fixing slits 175, 175 and fixing the cover 173, the plates 15, 17,
As shown in Figs. Part 129).

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 (rightward) 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 mounting member 135, and the mounting member 135 is fixed to the differential carrier 5 by the bolt 137. 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 intermittently operated, the controller controls the electric motor 27 in both directions (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 meshes with one end of the gear 107.

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.

In the state where the cam 21 is not operating, 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 functions 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.

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 engagement of the dog clutch 13 is released, 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 shock 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 center 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, holding surfaces (holding surface 115 and 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 dog clutch 13 and the 2-4 switching mechanism are disconnected, 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 flowing into the outer differential case 7 meshes with the gears 67, 69, 71 constituting 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 portion of the gear plate type actuator 1 is also immersed in the oil reservoir, 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 parts, the oil supplied reduces wear and improves durability, reduces frictional resistance at each sliding part, and improves fuel efficiency of the engine.

Thus, the structure for fixing the gear plate type actuator 1 to the differential carrier 5 and the rear differential 3 are constituted.

As described above, the structure for fixing the gear plate actuator 1 to the diff carrier 5 is such that the fixing plate portion 91 of the support plate 15 is engaged with the fixing slit 175 of the diff carrier 5 (casing member 171).
Assembly of the support plate 15 (each plate 15, 17, 19) to the differential carrier 5 and positioning in the axial direction and the radial direction are extremely easily completed. As described above, according to the present invention, assembly by bolting is performed. Therefore, the number of assembling steps is extremely small, and the assembling cost is significantly reduced.

Also, the number of parts and the cost are reduced by the number of bolts.

Further, since the support plate 15 does not need a bolt seat, the shape is simple and the cost is low, the differential carrier 5 does not need to be processed with a screw hole, and the support plate 15 is processed with a bolt through hole. Becomes unnecessary and the processing cost is reduced.

Further, due to the rotation stopping function of the cover 173, the operation of the gear plate type actuator 1 is stable,
The durability is improved.

Further, 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 leak, 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 structure for fixing the gear plate type actuator of the present invention to the differential carrier, the operated device is not limited to the clutch.

Further, the clutch is not limited to the meshing clutch (dog clutch) as in each embodiment, but may be a friction clutch such as a multi-plate clutch or a cone clutch.

Further, 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.

[0137]

According to the structure for fixing the gear plate type actuator to the differential carrier according to the first aspect of the present invention, the supporting portion of the supporting plate is simply engaged with the fixing slit on the side of the differential carrier, whereby the supporting plate of the supporting plate can be very easily formed. Assembly and axial positioning is complete.

Further, since bolting is not used for the assembling, the number of assembling steps and the assembling cost are greatly reduced.

Further, the support plate which does not require the seat for the bolt has a simple shape and is low in cost, and the processing cost of the differential carrier and the support plate is reduced.

According to the structure for fixing the gear plate type actuator to the differential carrier described in claim 2, it is possible to obtain the same effect as that of the structure of claim 1.

Further, since the support plate is prevented from rotating, the operation is stabilized and the durability is improved.

The structure for fixing the gear plate actuator to the differential carrier according to the third aspect can obtain the same effect as that of the structure according to the first or second aspect.

In addition to the axial positioning function of the fixing slit, the wedge positioning contact portion between the fixing slit and the support portion provides a radial positioning function.

The structure for fixing the gear plate type actuator described in claim 4 to the differential carrier is defined in claim 1
It is possible to obtain the same effect as that of the configuration of 3.

By utilizing the outer circumference of the operated device for radial positioning, radial positioning can be performed at low cost.

The power connection / disconnection device of a fifth aspect of the present invention is the first to fourth aspects of the present invention.
Similar to the configuration of (1), the support plate can be assembled very easily, and the effects such as simple structure, light weight, low cost, and improved reliability can be obtained.

In the differential device according to claim 6, like the constructions according to claims 1 to 4, assembling of the support plate is extremely easy, and at the same time, the structure is simple, the weight is low, the cost is low, and the reliability is improved. be able to.

In the differential device according to claim 7, like the constructions according to claims 1 to 4, assembling of the support plate is extremely easy, and at the same time, the structure is simple, the weight is low, the cost is low and the reliability is improved. be able to.

In the differential device according to claim 8, as with the structure according to claims 1 to 4, the support plate is extremely easy to assemble, and further, the structure is simple, the weight is low, the cost is low, and the reliability is improved. be able to.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a structure for fixing a gear plate actuator of one embodiment to a diff carrier and a rear diff 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 taken along line DD of FIG.

17 is a view on arrow E of FIG.

FIG. 18 is a sectional view of a conventional example.

[Explanation of symbols]

1 Gear Plate Actuator 3 Rear Differential (Differential Device) 5 Differential Carrier 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) ) 27 electric motor 29 gear set 91 fixed plate portion 91 (support portion) 99 gear plate 171 casing member (first constituting differential carrier)
Member) 173 Cover (second member constituting differential carrier) 175 Fixing slit 177 Wedge-shaped contact part (contact part between support part and fixing slit)

Claims (8)

[Claims] 1. An annular support plate fixed to a differential carrier, a cam plate arranged on one side in the axial direction of the support plate so as to be rotatable forward and backward, and an axial movement to the other side in the axial direction of the support plate. 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 gear plate type including an electric motor that rotates in forward and reverse directions, and 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 structure for fixing an actuator to a diff carrier, wherein a fixing slit is provided on an inner wall of the diff carrier, a support portion is provided on the support plate, and the support is provided. From being engaged in the fixing slits the parts, fixed structure to the differential carrier of the gear plate actuator, characterized in that fixing the support plate to the differential carrier. 2. The invention according to claim 1, wherein the diff carrier has a first member and a second member, the fixing slit is provided in the first member, and the diff carrier is fixed. To a differential carrier of a gear plate type actuator, characterized in that the support plate is prevented from rotating by fixing the second member to the first member after engaging the support portion of the support plate with the slit for use. Fixed structure. 3. The invention according to claim 1 or 2, wherein a wedge-shaped contact portion is formed between the fixing slit of the differential carrier and the support portion of the support plate, A structure for fixing a gear plate type actuator to a differential carrier, wherein a support plate is positioned in the radial direction with respect to the differential carrier. 4. The invention according to any one of claims 1 to 3, wherein the support plate, the cam plate, and the movable plate are each formed in an annular shape, and the outer periphery of the operated device. The structure for fixing the gear plate type actuator to the differential carrier is characterized in that it is positioned in the radial direction by. 5. A gear plate actuator, comprising: a pair of torque transmission members; and a clutch arranged between the torque transmission members, 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. 6. An outer differential case that rotates by receiving a driving force of a prime mover, an inner differential case that is relatively rotatably disposed 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 each other, and a gear plate type actuator according to any one of claims 1 to 4, 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. 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 to a wheel side from a pair of output side gears, 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 4, 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. 8. A differential case that rotates by receiving a driving force of a prime mover, a differential mechanism that distributes 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 type actuator having the clutch as an operated device according to any one of claims 1 to 4, wherein the clutch is disposed between the gear plate and the clutch. A differential device characterized in that the differential of the differential mechanism is limited by the operation of the clutch by a rotary actuator.