JP2003287103A - Gear plate type actuator and motive power intermitting device using this actuator and differential device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To inexpensively constitute a simple structure for improving installing performance. <P>SOLUTION: This structure has plates 15, 17, and 19, an electric motor 27 for rotatably operating the plate 17 via gears 153 and 107, a cam mechanism 21 for converting rotation of the plate 17 into moving operation force of the plate 19, an inserting hole 93 of the plate 15, an inserting hole 101 of the plate 17, a projection 103 of the plate 17, and a projection 121 of the plate 19. The plate 17 engages with the plate 15 by the projection 103 inserted into the inserting hole 93, and the plate 19 engages with the plate 17 by the projection 121 inserted into the respective inserting holes 93 and 101 of the plates 15 and 17. <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 an 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. To a differential device that limits

[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.

[0009]

[Problems to be Solved by the Invention] Actuator 101
3 is the cylinder 1017 and the piston 10 as described above.
19 and the shift fork 1021, and the like. Assembly of the actuator 1013 itself and assembly of the actuator 1013 with respect to the differential carrier 1003 involve many steps and are troublesome.

Further, the actuator 1013 requires a shift mechanism including the shift fork 1017, has a large number of parts, has a complicated structure, and is expensive, and in particular, an air pump is about 3 times the cost. Account for

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 dog 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 leakage, in order to prevent the pressure leakage, 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.

Further, in the differential device 1001, when the operating system such as the air pump, the actuator 1013, and the shift mechanism fails, the meshing of the meshing clutch 1011 is released by the return spring, and the vehicle returns to the two-wheel drive state. There is.

As described above, in the device for operating the clutch by the fluid pressure type actuator, when the operation system fails, the spring generally returns to another state (for example, if the clutch is connected by the actuator, the return spring is used). Since the clutch is disengaged), the state when the operation system is normal cannot be maintained.

Therefore, according to the present invention, it is extremely easy to assemble itself and the device to be operated, and it is constructed without using a piston and a cylinder, and the structure is simple, the cost is low, and the gear plate is highly reliable. Actuator,
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.

[0018]

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. A cam mechanism for converting into a movement operation force, the support plate is provided with a support plate side insertion hole, the cam plate is provided with a cam plate side insertion hole, A cam plate side projection that is inserted through the support plate side insertion hole and engages with the support plate at a circumferential position different from the support plate side insertion hole, and the movable plate is connected to the support plate side. While inserting each insertion hole on the side of the cam plate,
The movable plate side projections that engage with the cam plate are provided at different circumferential positions from the support plate side and the cam plate side insertion holes, and in the assembled state, the cam plate is inserted through the support plate side. The movable plate is engaged with the support plate by the cam plate side projection that is inserted through the hole, and the movable plate is connected to the cam plate by the movable plate side projection that is inserted through the insertion holes on the support plate side and the cam plate side. It is characterized in that they are engaged.

According to another aspect of the gear plate actuator of the present invention, the cam plate is engaged with the support plate by the projection by appropriately rotating the cam plate after inserting the projection on the cam plate side into the insertion hole on the support plate side. To meet.
Further, in this state, after the protrusion of the movable plate is inserted through the insertion holes of the support plate and the cam plate, if the cam plate is rotated in the opposite direction, for example, the movable plate will become the cam plate by the protrusion. Engage.

As described above, the assembly is extremely easy because no special tool is required, the number of steps is small.

In order to assemble the gear plate type actuator to the operated device, for example, the support plate may be fixed to the casing of the operated device with bolts or the like.
This is also very easy.

Further, the support plate, the cam plate, and the movable plate can all be press-worked (sheet-metal working), which is lighter in weight, and can be implemented at low cost.

Further, the gear plate type actuator of the present invention constructed to convert the rotating 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. It does not require expensive pumps, hydraulic actuators (piston and cylinder), shift mechanism, etc., and has a small number of parts, a simple structure, and 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 its routing space is not required, the gear plate type actuator and the operated device are lightweight and compact, and are easy to mount on the vehicle. 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.

The invention of claim 2 is the gear plate type actuator according to claim 1, wherein the cam mechanism comprises the movable plate side projection and a cam surface provided on the cam plate, When the cam surface rotates, the cam slope moves the movable plate in the axial direction through the movable plate side protrusion, and the movable plate side protrusion that moves on the cam slope is moved to the moving position. It is characterized by comprising a holding surface having no cam angle for holding, and it is possible to obtain the same operation and effect as the constitution of claim 1.

When the cam plate is pressed, the cam surface (cam piece) can be simultaneously pressed at low cost.

Further, the cam slope can adjust the cam angle both during and after machining, for example, according to the magnitude of the operating force required for the operated device, the torque of the electric motor, and the like. By adjusting the cam angle, it is possible to reduce the capacity of the electric motor, reduce the weight of the device, and reduce the load on the battery.If the operated device is an in-vehicle device, the fuel consumption of the engine that drives the alternator for charging the battery can be reduced. Can be improved.

If the holding surfaces having no cam angle are provided on both sides of the cam slope, the state of the cam mechanism can be stably maintained both before and after the operation even when the electric motor is stopped. By stopping the electric motor except when the cam mechanism is operated, the load on the battery and the alternator can be further reduced, and the fuel efficiency of the engine can be further improved.

A third aspect of the present invention is the gear plate type actuator according to the second aspect, wherein when the electric motor is not operated, the movable protrusion is abutted against the holding protrusion and the movable plate side protrusion. The plate-side protrusion is prevented from moving from the cam slope surface side to the holding surface and from the holding surface to the cam slope surface side.
It is possible to obtain the same operation and effect as the configuration of.

Further, since the check function is obtained by the holding projections provided between the inclined surface of the cam and the holding surface, even if a disturbance factor such as vibration or shock is received while the electric motor is stopped as described above. The cam mechanism is prevented from changing from the operating state to the non-operating state, or from changing from the non-operating state to the operating state.

Therefore, for example, when the differential device for operating the clutch for power connection and disconnection by the gear plate type actuator of the present invention is arranged on the side of the wheels that are disconnected during traveling in two-wheel drive in a four-wheel drive vehicle, vibration occurs during traveling. Even if a disturbance factor such as a shock or an impact is received, it is possible to prevent the four-wheel drive state from changing to the two-wheel drive state or the two-wheel drive state to the four-wheel drive state against the driver's intention.

A fourth aspect of the present invention is the gear plate actuator according to the second or third aspect, wherein the movable plate side projection has an axial portion formed on a base and the axial portion. 4. The structure according to claim 2 or claim 3, wherein the cam mechanism includes a radial portion formed at an end of the cam mechanism, and the cam mechanism includes the radial portion and the cam surface of the cam plate. The same action and effect can be obtained.

A fifth aspect of the present invention is the gear plate type actuator according to any one of the first to fourth aspects, wherein a plurality of the support plate side through holes are provided at equal intervals in the circumferential direction, and the cam is provided. A plurality of plate-side insertion holes are provided at equal intervals in the circumferential direction, a plurality of movable plate-side projections are provided at equal intervals in the circumferential direction, and a plurality of cam plate-side projections are provided at equal intervals in the circumferential direction. It is characterized in that it has the same operation and effect as those of the first to fourth aspects.

A sixth aspect of the present invention is the gear plate actuator according to any one of the first to fifth aspects, wherein the support plate, the cam plate, and the movable plate are each formed in an annular shape. The support plate side insertion hole is a recess formed in the inner periphery of the support plate, the cam plate side insertion hole is a recess formed in the inner periphery of the cam plate, and the periphery of the operated device. It is characterized in that it is coaxially arranged, and it is possible to obtain the same actions and effects as the constitutions of claims 1 to 5.

Further, since the support plate, the cam plate, and the movable plate are each formed in an annular shape, the gear plate type actuator can be coaxially arranged around the operated device, and the gear plate type actuator and the operated device can be arranged. The entire assembly of
In-vehicle performance is improved.

The invention according to claim 7 is the gear plate type actuator according to any one of claims 1 to 6, wherein the return spring biases the operated device to a non-operating state, and the return spring 7. A configuration according to claim 1, further comprising: a shift spring for operating the operated device against operation, wherein a cam thrust force of the cam mechanism acts in a direction of bending the shift spring. The same action and effect as can be obtained.

In addition, in this configuration in which a shift spring for operating the operated device is used and the shift spring is bent by the cam mechanism (the operated device is inactivated), for example, Even if the electric motor becomes out of order, the operated device is activated by the shift spring.

Therefore, for example, when the differential device for operating the clutch for power connection and disconnection by the gear plate type actuator of the present invention is arranged on the side of the wheels that are disconnected during two-wheel drive of a four-wheel drive vehicle, or the present invention If the power connection / disconnection device configured to engage and disengage the clutch with the gear plate type actuator is arranged in the power transmission system on the wheel side that is disconnected during two-wheel drive traveling, the electric motor will malfunction during four-wheel drive traveling. Also, since the vehicle is held in the four-wheel drive state by the shift spring, the failure mode is good.

When the operated device is a dog clutch, the shift spring serves as a waiting mechanism to reduce ratcheting and ratchet noise when the dog clutch is operated to mesh, thereby greatly improving durability.

The invention of claim 8 is the gear plate type actuator according to any one of claims 1 to 7, wherein the groove for engaging the end portion of the shift spring to prevent the shift spring from falling is provided. It is characterized in that it is provided on the plate and the movable plate respectively, and it is possible to obtain the same actions and effects as the configurations of claims 1 to 7.

Further, since the spring is prevented from falling off by the grooves provided in the support plate and the movable plate, the function of the gear plate type actuator is normally maintained.

Further, since the spring is positioned by the groove at the time of assembling, the assembling property is improved.

The invention of claim 9 is the gear plate type actuator according to any one of claims 1 to 8, wherein the position of the movable plate is detected between the support plate and the movable plate. Since the position sensor is arranged, the same operation and effect as those of the first to eighth aspects can be obtained.

Further, the position sensor detects the position of the movable plate, and the operated device (eg, clutch).
Since it is possible to directly know the state, it is possible to prevent the electric motor from continuing to rotate more than necessary by immediately stopping the electric motor after moving the movable plate by the electric motor.

Therefore, the excessive rotation of the electric motor, the hit of the gear set due to the excessive rotation, the overcurrent of the electric motor due to the hit of the gear set, the deterioration of the durability of the electric motor, etc. are prevented, and the load on the battery is reduced.

Further, between the movable plate and the support plate on which the position sensor is arranged, unlike the structure in which the position sensor is arranged between the cam plate and the cam plate, relative rotation does not occur with the position sensor interposed, so that the sliding movement is prevented. Wear of the position sensor due to movement is prevented, and carburizing / quenching to improve wear resistance and surface hardening treatment such as nitriding treatment are not required, and the cost increase due to these is avoided.

Further, it is possible to prevent an increase in the load on the electric motor, the battery, the alternator, etc., and a decrease in fuel consumption due to the sliding resistance of the position sensor.

Further, the position sensor attached to the support plate (on the gear plate type actuator) does not need to be aligned with the operated device upon assembling, which facilitates the assembling.

The invention of claim 10 is the gear plate actuator according to any one of claims 1 to 9, characterized in that the cam plate and the gear plate are integrally formed. Therefore, it is possible to obtain the same operation and effect as the configurations of claims 1 to 9.

Further, by integrally forming the cam plate and the gear plate, the number of parts and the cost can be reduced.

According to an eleventh aspect of the present invention, there is provided a power connection / disconnection device according to any one of the first to tenth 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.

As described above, the power connecting / disconnecting device of the eleventh aspect is arranged in the power transmission system on the wheel side which is disconnected when the vehicle is driven by the four-wheel drive and driven by the two-wheel drive. If so, the vehicle will be in a four-wheel drive state, and if the clutch is disengaged, the vehicle will be in a two-wheel drive state.

Further, the power connection / disconnection device according to claim 11 uses the gear plate type actuator according to claims 1-10, so that assembling is very easy, the structure is simple, It is possible to obtain effects such as light weight, low cost, and improved reliability.

A differential device according to a twelfth aspect of the present invention is an outer differential case which is rotated by receiving a driving force of a prime mover,
11. An inner diff case, which is rotatably disposed inside the outer diff case, a differential mechanism connected to the inner diff case, a clutch for connecting and disconnecting the outer diff case and the inner diff case, and And a gear plate type actuator having the clutch as a device to be operated, wherein the torque is interrupted between the outer differential case and the inner differential case by operating the clutch by the gear plate type actuator. Is characterized by.

According to a twelfth aspect of the present invention, the differential device is a differential device which intermittently drives the driving force on the input side of the differential mechanism, and as described above, the power transmission on the wheel side which is disconnected during two-wheel drive of a four-wheel drive vehicle. When the clutch is connected by the gear plate type actuator of the present invention, the vehicle is in a four-wheel drive state, and when the clutch is disconnected, the vehicle is in a two-wheel drive state.

The differential device according to claim 12 uses the gear plate type actuator according to claims 1 to 10, so that the assembly is extremely easy, the structure is simple, and the weight is the same as the structure according to claims 1 to 10. It is possible to obtain effects such as low cost and improved reliability.

In the differential device according to a thirteenth aspect, any one of 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 the output side gears. A clutch arranged between one of the wheels and the wheel thereof,
And a gear plate type actuator having the clutch as a device to be operated, and the torque is intermittent between the side gear and the wheel by the operation of the clutch by the gear plate type actuator. It has a feature.

Further, the differential device according to claim 13 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 12, when the vehicle is driven by two wheels in four-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 4
When the vehicle is in the wheel drive state and the clutch is disengaged, the driving force is interrupted by the differential rotation of the differential mechanism, and the vehicle is in the two wheel drive state.

Further, the differential device according to claim 13 uses the gear plate type actuator according to claims 1 to 10, so that the assembly is extremely easy, the structure is simple, and the weight is the same as the structure according to claims 1 to 10. It is possible to obtain effects such as low cost and improved reliability.

According to a fourteenth aspect of the present invention, in the differential device, 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, 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 claim 1, 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 of the fourteenth 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 connection of the clutch is released.

Further, the differential device of claim 14 uses the gear plate type actuator of claims 1 to 10, so that assembling is very easy, the structure is simple, and the weight is the same as the structure of claims 1 to 10. It is possible to obtain effects such as low cost and improved reliability.

A fifteenth aspect of the present invention is the power connecting / disconnecting device or the differential device according to any one of the eleventh to fourteenth aspects, wherein the torque transmission member, the outer differential case, or the differential case is Is supported by a stationary member via a thrust bearing and a bearing cap, and the bearing cap is screwed to the stationary member by a screw portion, and the bearing cap is provided with the cam plate or the movable member. By providing the abutment portion with the plate or the support plate, when the bearing cap is rotated by the screw portion to adjust the preload of the thrust bearing, the abutment portion of the bearing cap is pressed. The cam plate or the movable Rate, or the support plate, and characterized by moving by a stroke of the bearing cap and the same amount, it is possible to obtain a structure the same operation and effect of claim 11 to 14.

According to the fifteenth aspect of the present invention, as described above, even when the outer differential case, the torque transmitting member, and the differential case move when the preload of the thrust bearing is adjusted by rotating the bearing cap with the screw portion, The abutment part provided on the bearing cap is the cam plate,
Alternatively, the movable plate or the support plate is hit, and these move by the same stroke as the bearing cap.

Therefore, even if the torque transmission member, the outer differential case, and the differential case move before and after the preload adjustment, the distance between each plate (cam plate, movable plate, and support plate) and the torque transmission member, the outer differential case, and the differential case. Is maintained at a predetermined value, for example,
The spring force of the shift spring that presses the clutch is maintained at an appropriate value, and the operation of the gear plate actuator is normally maintained.

[0069]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS [First Embodiment] A gear plate type actuator 1 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 four-wheel drive vehicle in which the rear differential 3 is used and the left and right directions in FIG. Further, members and the like not given reference numerals in the following description are not shown.

The rear differential 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 driving force 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 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 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 consisting 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. When these bearing caps 37 are rotated 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.

On the left and right sides of the outer differential case 7, openings 57 and 59 through which oil flows in and out are provided 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 through 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, pinion gears 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.

Thrust washers 85 are arranged between the side gears 69 and 71 and the outer differential case 7, respectively, and receive the thrust force of meshing between the side gears 69 and 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 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 (support plate side insertion holes) provided on the inner periphery of the annular plate portion 89 at equal intervals in the circumferential direction, and two assembly recesses 93 provided on the outer periphery of the annular plate portion 89 at equal intervals in the circumferential direction. It is composed of a guide groove 95 and the like.

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 are provided 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.

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.
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 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.

Each fixing plate portion 91 of the support plate 15 is fixed to the differential carrier 5 by bolts 137 together with the mounting bracket 135 of the electric motor 27, as shown in FIG.

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 (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.

As the return spring 23 and the shift spring 25, a coil spring 145 and a coil spring 147 may be used, 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 bracket 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, 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 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 the electric motor 27 is stopped while the vehicle is running. 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 (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 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 and the free rotation state is performed. 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 side 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 side 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.
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 part 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 sections, the oil supplied reduces wear and improves durability, reduces frictional resistance at each sliding section, and improves fuel efficiency of the engine.

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

The gear plate actuator 1 is assembled by mounting the cam plate 17 on the support projection 103 as described above.
Through the mounting recesses 93 of the support plate 15 and twisted slightly to move the cam guide piece 121 of the movable plate 19 into the mounting recesses 93, 1 of the support plate 15 and the cam plate 17.
Since it is completed by simply twisting the cam plate 17 through 01, no special tool is required, the number of steps is small, and it is extremely easy.

Further, when the gear plate type actuator 1 is assembled to the rear differential 3, the support plate 15 is bolted to the differential carrier 5, the electric motor 27 is fixed to the differential carrier 5 with the mounting bracket 135, and the pinion gear 153 is attached to the cam plate 17 side. This is extremely easy because it only needs to engage with the gear 107 of.

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 differential 3 using No. 1 does not require a wide space for arranging pressure lines and the like, and is lightweight and compact to improve the vehicle mountability. Moreover, it is not necessary to change the diff carrier 5, and a large cost for the change. The rise is prevented.

Further, the gear plate type actuator 11
The rear diff 3 and the rear diff 3 are released from the effects of functional deterioration and pressure fluctuation due to pressure leakage, greatly improving performance, stability and reliability, and avoiding the strengthening of seals in each part of the pressure line and the accompanying increase in cost. To be

Further, the support plate 15 and the cam plate 1
7. The movable plate 19 is all processed by sheet metal processing, which is lightweight and low cost.

The cam piece 105 of the cam plate 17 can also be processed at low cost by pressing.

Furthermore, the inclined surface 113 of the cam piece 105 is
The cam angle can be adjusted according to the magnitude of the operating force (the cam thrust force with respect to the biasing force of the shift spring 25) required for the dog clutch 13 and the torque of the electric motor 27, both during and after processing. By adjusting the cam angle, it is possible to reduce the capacity of the electric motor 27, reduce the load on the battery and the charging alternator, and improve the fuel efficiency of the engine.

Further, on the holding surfaces provided on both sides of the inclined surface 113 of the cam piece 105 and having no cam angle, no rotational torque is applied to the cam piece 105 (cam plate 17), and the state of the cam 21 is before and after the operation. Cam 2 because it is held by both
After operating 1, the electric motor 27 can be stopped, the load on the battery and the alternator is further reduced, the fuel consumption is further improved, and the durability of the electric motor 27 is improved.

Further, even if the electric motor 27 is stopped, or even if the electric motor 27 fails, the holding function allows the vehicle to be stably held in the four-wheel drive state and the two-wheel drive state.

Also, the holding projection 11 provided on the cam piece 105.
The check function of 7 prevents the vehicle from changing from the two-wheel drive state to the four-wheel drive state against the driver's intention even if the vehicle receives a vibration or a shock.

Also, the support plate 15 and the cam plate 1
By forming the movable plate 19 and the movable plate 19 in an annular shape, the gear plate type actuator 1 can be installed in the rear differential 3
It becomes possible to arrange coaxially around the (boss portion 33), the rear differential 3 becomes compact as much, and the vehicle mountability is improved.

Further, the shift spring 25 serves as a waiting mechanism to reduce ratcheting and ratchet noise when the dog clutch 13 is engaged with each other, and durability is greatly improved.

Also, the cam plate 17 and the gear plate 9
By integrally forming 9 and 9, the number of parts and the cost are reduced.

[Second Embodiment] FIG. 16 shows a gear plate type actuator 1 and a rear differential 201 using the same.
(Differential device) will be described.

The rear differential 201 is used in the four-wheel drive vehicle in which the rear differential 3 of the first embodiment is used in place of the rear differential 3, and hereinafter, the same members and the like as the rear differential 3 are given the same reference numerals. The differences will be explained while citing.

Bearing caps 203, 203 are screwed to the diff carrier 5 by screw parts 39,
The boss portions 31 and 33 of the outer differential case 7 are supported by the differential carrier 5 via a thrust bearing 35 and a bearing cap 203, respectively. As shown in FIG. 16, each bearing cap 203 also serves as an outer race of each thrust bearing 35.

Further, in each bearing cap 203,
An abutting portion 205 that contacts the cam plate 17 is provided.

These bearing caps 203, 20
By rotating 3 with the screw portion 39, the outer races (bearing caps 203) of the left and right thrust bearings 35 are moved in the axial direction, and preload adjustment is performed.

Further, even if the outer differential case 7 moves due to this preload adjustment, the bearing cap 2
The cam plate 17 is pushed by the abutting portion 205 of 03 to bend the support plate 15, and the cam plate 17 and the movable plate 19 move by the same stroke as the bearing cap 203 (outer differential case 7).

Therefore, before and after the preload adjustment, the gap 207 between the retainer 139 on the dog clutch 13 side and the movable plate 19 is kept at a predetermined value, and the clutch ring 51 is kept.
Since the spring force of the shift spring 25 that presses is maintained at an appropriate value, the gear plate actuator 1
Works fine.

[Third Embodiment] A gear plate actuator according to the third embodiment will be described with reference to FIG.

The gear plate type actuator of the third embodiment is obtained by adding a position sensor 301 to the gear plate type actuator 1.

The position sensor 301 is a position switch and is screwed to the support plate 15. Further, the probe 303 comes into contact with the movable plate 19,
The signal line 305 is connected to the controller.

As described above, the movable plate 19 is bidirectionally moved and operated by the shift spring 25 and the cam 21 to move to the connection position (four-wheel drive position) and the connection release position (two-wheel drive position) of the dog clutch 13. Then, the probe 303 interlocked with the movable plate 19 activates the switch, and the ON-OFF signal is sent from the signal line 305 to the controller.

After operating the dog clutch 13 with the electric motor 27, the controller detects the position sensor 301.
From the ON-OFF signal received from the movable plate 19
Is detected (the dog clutch 13 is in a target state), and the rotation of the electric motor 27 is stopped.

As described above, since the state of the dog clutch 13 (the discontinuous state of the rear differential 3) can be directly known by the position sensor 301, the electric motor 27 can be immediately stopped after the dog clutch 13 is operated. , Over-rotation of the electric motor 27, gear set 2 due to over-rotation
Electric motor 27 by hitting 9 and hitting gear set 29
Is prevented, the durability of the electric motor 27 is reduced, and the burden on the battery is reduced.

Further, since relative rotation does not occur between the movable plate 19 and the support plate 15 to which the position sensor 301 is attached, the position sensor 301 by sliding
Wear of the (probe 303) is prevented, and carburizing / quenching for improving wear resistance and surface hardening treatment such as nitriding treatment are not necessary, and cost increase due to these is avoided.

Further, it is possible to prevent an increase in load on the electric motor 27, the battery, the alternator, etc., and a decrease in fuel consumption due to the sliding resistance of the position sensor 301.

The position sensor 30 attached to the support plate 15 (on the gear plate type actuator)
1 does not need to be aligned with the rear differential 3 for assembling, and thus the assembling is easy.

[Fourth Embodiment] A gear plate actuator according to a fourth embodiment will be described with reference to FIGS. 18 and 19.

The gear plate type actuator of the fourth embodiment is a modification of the gear plate type actuator 1, and a scrowave spring 401 is used in place of the shift spring 25.

This scroll wave spring 401 is
It is arranged between the support plate 15 and the movable plate 19 and biases the clutch ring 51 to the coupling side of the dog clutch 13 via the movable plate 19. As shown in FIG. 19, the scroll wave spring 401 has tip portions 407 and 409 formed when the spring material is cut.

Also, the support plate 15 and the movable plate 1
9 are provided with circumferential grooves 403 and 405, respectively, and the tip portion 40 of the scroll wave spring 401 is provided.
7,409 are engaged with these grooves 403,405.

As described above, since the tips 407 and 409 of the scroll wave spring 401 are positioned by the grooves 403 and 405 provided in the support plate 15 and the movable plate 19, the movable plate 19 moves (the dog clutch 13 moves). Even if the scroll wave spring 401 repeatedly expands and contracts due to (intermittent operation), the tip portions 407, 4
Since the fall of 09 is prevented, the scroll wave spring 401 is held at a predetermined position, and the function of the gear plate type actuator is normally maintained.

Further, at the time of assembling, the scroll wave spring 401 (tips 407 and 409) is fitted into the grooves 403 and 4.
Since it is positioned by 05, it is easy to assemble.

In the gear plate type actuator of the present invention, 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.

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.

[0183]

In the gear plate type actuator according to the first aspect of the present invention, assembling the support plate, the cam plate and the movable plate does not require a special tool, requires few steps, and is extremely easy.

Also, the gear plate type actuator can be assembled very easily, for example, only by fixing the support plate to the casing of the operated device.

Further, the support plate, the cam plate and the movable plate can all be press-worked, so that they are constructed lighter and can be implemented at low cost.

Further, unlike the structure using the fluid pressure type actuator, an expensive pump, piston and cylinder,
No shift mechanism is required, the number of parts is small, the structure is simple, and the cost is low.

Further, the operated device using the gear plate type actuator has a wide arrangement space such as a pressure line.
It is not necessary to use a housing, is light in weight and is compact in size, improves the vehicle mountability, and eliminates the need to change the casing, which prevents a large increase in cost due to the change.

Further, the gear plate type actuator and the operated device are released from the influence of the function deterioration and the pressure fluctuation due to the pressure leak, 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.

According to the gear plate type actuator of the second aspect, it is possible to obtain the same effect as that of the configuration of the first aspect.

When the cam plate is pressed, the cam surface can also be pressed at a low cost at the same time.

Further, the cam slope allows the cam angle to be adjusted both during and after machining, which can reduce the capacity of the electric motor, reduce the weight of the device, and reduce the burden on the battery. In the case of an in-vehicle device, it is possible to improve the fuel efficiency of the engine that drives the alternator for charging the battery.

If the holding surfaces having no cam angle are provided on both sides of the cam slope, the state of the cam mechanism is stably maintained both before and after the operation, and the cam mechanism is electrically operated except when the cam mechanism is operated. By stopping the motor, the load on the battery and alternator can be further reduced, and fuel consumption can be further improved.

According to the gear plate type actuator of claim 3, it is possible to obtain the same effect as that of the structure of claim 2.

Further, by the function of checking the holding projection,
Since the cam mechanism is prevented from changing from the operating state to the non-operating state, or from changing from the non-operating state to the operating state, the power connection / disconnection device for operating the clutch for power connection / disconnection with the gear plate actuator of the present invention. With a differential device, even if you receive vibrations or shocks while running,
It is possible to prevent the four-wheel drive state from changing to the two-wheel drive state or the two-wheel drive state to the four-wheel drive state against the driver's intention.

According to the gear plate type actuator of claim 4, it is possible to obtain the same effect as that of the configuration of claim 2 or 3.

According to the gear plate type actuator of the fifth aspect, the same effects as those of the first to fourth aspects can be obtained.

According to the gear plate type actuator of claim 6, it is possible to obtain the same effects as those of the structures of claims 1 to 5.

Further, the annular gear plate type actuator can be coaxially arranged around the operated device, the entire assembly of the gear plate type actuator and the operated device becomes compact, and the vehicle mountability is improved. To do.

The gear plate type actuator of the seventh aspect can obtain the same effects as those of the first to sixth aspects.

Further, in this structure in which the shift spring is bent by the cam mechanism, even if the electric motor malfunctions,
Since the operated device is activated by the shift spring, in the case of a power disconnecting device or a differential device in which the gear plate actuator of the present invention operates the clutch for power disconnecting, the electric motor becomes out of order during four-wheel drive traveling. Also, since the vehicle is held in the four-wheel drive state by the shift spring, the failure mode is good.

Further, when the dog clutch is operated, the shift spring serves as a waiting mechanism, which reduces ratcheting and ratchet noise when the dog clutch is operated, greatly improving durability.

According to the gear plate type actuator of claim 8, it is possible to obtain the same effects as those of the structures of claims 1 to 7.

Further, the grooves provided in the support plate and the movable plate prevent the spring from coming off, the function of the gear plate type actuator is normally maintained, and the spring is positioned at the time of assembling. Is good.

The gear plate type actuator of the ninth aspect can obtain the same effects as those of the first to eighth aspects.

Also, the position of the movable plate (the state of the operated device) can be directly known by this position sensor, and the electric motor is immediately stopped after the movable plate is moved, whereby the electric motor is over-rotated or over-rotated. It is possible to prevent the gear set from hitting due to the rotation, the overcurrent of the electric motor due to the hit of the gear set, the deterioration of the durability of the electric motor, and the like, and to reduce the load on the battery.

Further, since the position sensor arranged between the support plate and the movable plate which do not rotate relative to each other does not wear due to sliding, surface hardening treatment for improving wear resistance is unnecessary. Therefore, the increase in cost can be avoided and the electric motor by the sliding resistance of the position sensor,
It also prevents the burden on the battery and alternator from increasing, and the reduction in fuel consumption.

Further, the position sensor attached to the support plate (on the gear plate type actuator) does not need to be aligned with the operated device in assembling, and the assembling property is good.

According to the gear plate type actuator of the tenth aspect, it is possible to obtain the same effects as the configurations of the first to ninth aspects.

Further, by integrally forming the cam plate and the gear plate, the number of parts and the cost can be reduced.

The power connection / disconnection device according to claim 11 is characterized by that
By using the gear plate type actuator of 10, extremely easy assembly, simple structure, lightweight, low cost,
It is possible to obtain effects such as improved reliability.

The differential device according to claim 12 uses the gear plate type actuator according to claims 1 to 10, whereby the assembly is extremely easy, the structure is simple, the weight is light, the cost is low, and the reliability is improved. it can.

The differential device according to claim 13 uses the gear plate type actuator according to claims 1 to 10, whereby the assembly is extremely easy, the structure is simple, the weight is light, the cost is low, and the reliability is improved. it can.

The differential device according to claim 14 uses the gear plate type actuator according to claims 1 to 10, whereby the assembly is extremely easy, the structure is simple, the weight is light, the cost is low, and the reliability is improved. it can.

According to the fifteenth aspect of the invention, it is possible to obtain the same effects as those of the eleventh to fourteenth aspects.

Even if the preload adjustment is performed, the spring force of the shift spring that presses the operated device is maintained at an appropriate value, and the operation of the gear plate type actuator is normally maintained.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a gear plate actuator and a rear differential using the same according to a first embodiment.

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

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 each embodiment.

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

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

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

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

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;

FIG. 16 is a cross-sectional view showing a gear plate actuator and a rear differential using the same according to a second embodiment.

FIG. 17 is a diagram showing a position sensor and its mounting state in the third embodiment.

FIG. 18 is a view showing a support plate and a movable plate in the fourth embodiment.

FIG. 19 is a view on arrow D in FIG. 18.

FIG. 20 is a sectional view of a conventional example.

[Explanation of symbols]

1 Gear plate type actuator 3 Rear differential (differential device) 7 outer differential case 9 inner differential case 11 Bevel gear type differential mechanism 13 dog clutch (device to be operated: clutch) 15 Support plate 17 Cam plate 19 Movable plate 21 cam (cam mechanism) 23 Return spring 25 shift springs 27 electric motor 29 gear sets 93 Assembly recess (support plate side insertion hole) 99 gear plate 101 Assembly recess (cam plate side insertion hole) 103 Support protrusion (Cam plate side protrusion) 105 cam pieces 107 Gear on Gear Plate 115 Holding surface without cam angle 121 Cam guide piece (movable plate side protrusion) 127 Axial part of cam guide piece 129 Cam guide piece radial part 147 Coil spring (shift spring) 201 Rear differential (differential device) 203 bearing cap 205 butting part 301 Position sensor 403 Grooves provided on the support plate 405 Grooves provided on the movable plate

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Satoshi Tomita             2388 Omiyamachi, Tochigi City, Tochigi Prefecture Tochigi Fuji             Business F term (reference) 3D043 AA05 AA06 AA07 AA10 EA02                       EA17 EA38 EA43 EA45 EB03                       EB07 EB12                 3J027 FA17 FA18 FA19 FB01 HA01                       HB07 HC21 HC22 HD01 HE05                       HF44 HG07                 3J062 AA01 AB03 AB31 AC07 BA11                       CG17

Claims (15)

[Claims] 1. An annular support plate fixed to a stationary side, a cam plate rotatably and rotatably arranged on one side of the support plate in the axial direction, and an axial direction on 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 support plate side insertion hole is provided in the plate, a cam plate side insertion hole is provided in the cam plate, the support plate side insertion hole is inserted in the cam plate, and A cam plate side protrusion that engages with the support plate at a circumferential position different from the holding plate side insertion hole is provided, and the support plate side and the cam plate side insertion holes are inserted into the movable plate, and A movable plate side projection that engages with the cam plate is provided at different circumferential positions from the support plate side and the cam plate side insertion holes, and the cam plate is inserted into the support plate side insertion hole in the assembled state. Is engaged with the support plate by the cam plate side projection that is inserted through, and the movable plate is engaged with the cam plate by the movable plate side projection that is inserted through the insertion holes on the support plate side and the cam plate side. Gear plate type actuator characterized by matching. 2. The invention according to claim 1, wherein the cam mechanism includes the movable plate side protrusion and a cam surface provided on the cam plate, and the cam surface is the cam plate. Rotation, the cam slope that moves the movable plate in the axial direction through the protrusion on the movable plate side, and the cam angle that holds the protrusion on the movable plate side that has moved on the cam slope in the moving position without a cam angle And a gear plate type actuator. 3. The invention according to claim 2, wherein a holding projection is provided between the cam slope of the cam surface and the holding surface, and the holding projection and the holding projection are provided when the electric motor is not operated. A gear plate actuator, characterized in that, by abutting against the movable plate side projection, movement of the movable plate side projection from the cam slope side to the holding surface and from the holding surface to the cam slope side is prevented. 4. The invention according to claim 2 or claim 3, wherein the movable plate side projection has a diameter formed at an axial portion formed on a base portion and an end portion of the axial portion. A gear plate actuator comprising: a directional portion, wherein the cam mechanism includes the radial portion and the cam surface of the cam plate. 5. The invention according to claim 1, wherein a plurality of the support plate side insertion holes are provided at equal intervals in the circumferential direction, and the cam plate side insertion holes are in the circumferential direction. A plurality of gear plates are provided at equal intervals, the movable plate side projections are provided at equal circumferential intervals, and the cam plate side projections are provided at equal circumferential intervals. Actuator. 6. The invention according to claim 1, wherein the support plate, the cam plate, and the movable plate are each formed in an annular shape, and the support plate-side insertion hole includes: It is a recess formed in the inner periphery of the support plate, the cam plate side insertion hole is a recess formed in the inner periphery of the cam plate, and is arranged coaxially around the operated device. Characteristic gear plate type actuator. 7. The invention according to claim 1, further comprising: a return spring for urging the operated device to a non-operating state, and the operated device against the return spring. A gear plate actuator, comprising a shift spring for operating the cam plate, wherein a cam thrust force of the cam mechanism acts in a direction of bending the shift spring. 8. The invention according to claim 7, wherein grooves for engaging the ends of the shift spring to prevent the shift spring from falling off are provided in the support plate and the movable plate, respectively. Gear plate type actuator. 9. The invention according to claim 1, wherein a position sensor for detecting a position of the movable plate is arranged between the support plate and the movable plate. Gear plate actuator. 10. The invention according to claim 1, wherein the cam plate and the gear plate are formed integrally with each other. 11. 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. 12. 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. A clutch for connecting and disconnecting the inner differential case and the inner differential case; and a gear plate type actuator according to any one of claims 1 to 10, wherein the clutch is 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. 13. 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 type actuator according to any one of claims 1 to 10, wherein the clutch is an operated device, and the side gear is operated by operating the clutch by the gear plate type actuator. A differential device characterized by intermittent torque between a wheel and a wheel. 14. 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 actuator that is disposed between the clutch and 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. 15. The invention according to claim 11, wherein the torque transmission member, the outer differential case, or the differential case is located on a stationary side via a thrust bearing and a bearing cap. The bearing cap is supported by a member, and the bearing cap is screwed to the stationary side member by a screw portion, and the bearing cap is abutted with the cam plate, the movable plate, or the support plate. By providing the, when adjusting the preload of the thrust bearing by rotating the bearing cap with the screw portion,
The differential device, wherein the cam plate, the movable plate, or the support plate is pushed by the abutting portion of the bearing cap and moves by the same stroke as the bearing cap.