JP2003232431A - Actuator, and differential device using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To hold a clutch in a connected state even when a pushing pressure source is stopped. <P>SOLUTION: This actuator is provided with the pushing pressure source to push and connect the clutch 11, connection holding means 15, 17, and 19 to hold the clutch 11 in the connected state as the clutch 11 is connected by receiving pushing pressure of the pushing pressure source as connection of the clutch 11 is released, and connection releasing means 15, 17, and 19 to return the clutch 11 to a connection released state by receiving pushing pressure of the pushing pressure source as the clutch 11 is connected. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an actuator having a function of holding a connected state of a clutch, a differential device for connecting and disconnecting a driving force using the actuator, and a differential device for limiting a differential.

[0002]

2. Description of the Related Art FIG. 6 shows a conventional differential device 50.
1 is shown.

The differential device 501 is composed of a pneumatic or hydraulic actuator, an outer differential case 503, an inner differential case 505, a bevel gear differential mechanism 507, a dog clutch 509, a return spring 511 and the like.

The outer differential case 503 and the inner differential case 505 are arranged so as to be rotatable relative to each other. The outer differential case 503 is rotationally driven by the driving force of the engine, and the differential mechanism 507 is connected to the inner differential case 505.

The dog clutch 509 is a clutch ring 51 movably connected to an outer differential case 503.
3 and the inner differential case 505.

The actuator operates by being supplied with operating pressure from a pump driven by the engine, and the clutch ring 5
13 is moved to engage the dog clutch 509.

When the dog clutch 509 is engaged, the outer differential case 503 is rotated by the inner differential case 50.
5 and the differential mechanism 507 to distribute to the left and right wheels, and the vehicle enters the four-wheel drive state.

When the supply of operating pressure to the actuator is stopped, the dog clutch 509 is disengaged by the urging force of the return spring 511, the inner differential case 505 to the left and right wheels are separated from the engine side, and the vehicle becomes 2 Wheel drive state.

[0009]

The differential device 501 uses a pump to drive an actuator (pressing force source).
Is operated to resist the urging force of the return spring 511 and keep the dog clutch 509 in the connected state.

In such a structure, for example, when the pressing force source is a fluid pressure type actuator such as a pneumatic type or a hydraulic type, it is necessary to continue driving the pump in order to keep the clutch in the connected state. The fuel economy of the driven engine is reduced.

Further, it is necessary to detect the state where the pressure is constant by using the pressure switch for detecting the pressure of the pressure member, which increases the cost.

When an electromagnet is used as a pressing force source,
The load on the battery that excites the electromagnet and the alternator that charges the battery increases, and the fuel efficiency of the engine that drives the alternator decreases.

Further, conventionally, it has not been possible to detect whether the clutch is engaged or disengaged.

Therefore, according to the present invention, an actuator capable of holding the clutch in the engaged state even if the pressing force source for connecting the clutch is stopped, and a differential device for intermittently driving the driving force using the actuator are provided. The purpose of the present invention is to provide a differential device that limits movement.

[0015]

An actuator according to a first aspect of the present invention includes a clutch having a connected state and a disengaged state in which the connection is released, and a pressing force source that applies a pressing force to the clutch to bring the clutch into a connected state. An actuator provided with the connection holding means for holding the clutch in the connected state when the pressing force source receives the pressing force in a state where the clutch is disconnected, and the clutch. And a connection releasing means for returning the clutch to the connection released state when the pressing force of the pressing force source is received in the connected state.

When the pressing force of the pressing force source is applied to the clutch while the clutch is connected, the connection releasing means operates in response to this, and the clutch is returned to the connection released state. After that, when the pressing force of the pressing force source is applied to the clutch in the state where the clutch is disengaged in this way, the clutch is connected and the connection holding means operates to hold the clutch in the connected state.

As described above, in the actuator of the first aspect, since the clutch is held in the connected state by the connecting and holding means, the pressing force source can be stopped after the clutch is connected.

Therefore, when the pressing force source is a fluid pressure type actuator, the pump can be stopped immediately after the clutch is engaged, so that the fuel consumption of the engine for driving the pump can be prevented from decreasing.

Further, since the pressure switch for detecting the pressure of the pressure member is unnecessary, the cost is reduced accordingly.

Further, when the electromagnet is used as the pressing force source, the excitation of the electromagnet can be immediately stopped after the clutch is connected. Therefore, the burden on the battery for exciting the electromagnet and the burden on the alternator for charging the battery are increased. Is prevented, and a reduction in fuel consumption of the engine that drives the alternator is prevented.

In addition to the above, since the connection holding means and the connection releasing means operate alternately only by pressing the clutch by the pressing force source as described above, the operation of the connection holding means and the connection releasing means. No operating means for switching is required, and since the pressing force of the pressing force source is used for these switching, it is not necessary to separately provide a driving force source for switching.

Therefore, the actuator of the present invention has a simple structure and can be implemented at low cost.

According to a second aspect of the present invention, in the actuator according to the first aspect, the connection holding means and the connection releasing means are alternately arranged by a cam that operates by receiving the pressing force of the pressing force source. It is characterized by switching to each operating state, and it is possible to obtain the same operation and effect as the configuration of claim 1.

A third aspect of the invention is the actuator according to the first aspect, further comprising a clutch member that is moved by receiving the pressing force of the pressing force source to connect the clutch, and the connection holding means is provided. When the pressing force of the pressing force source is received in a state where the engagement portions provided on the clutch member and the counterpart member are disengaged from the clutch, the engagement portion engages with the engagement portion. An engagement member for keeping the clutch in a connected state, and the connection release means receives the pressing force of the pressing force source in a state in which the clutch is connected, and the engagement member and the engagement portion. It is characterized by having a cam for releasing the engagement of (1) and returning the clutch to the disengaged state, and it is possible to obtain the same operation and effect as the configuration of claim 1.

The invention according to claim 4 is the actuator according to any one of claims 1 to 3, characterized in that a sensor for detecting a connected state of the clutch is provided. It is possible to obtain the same operation and effect as the configuration of.

Further, since the sensor can detect the connected / disengaged state and the disengaged state of the clutch in real time, after the clutch is engaged and disengaged,
It becomes possible to immediately stop the operation of the pressing force source such as the pump or the electromagnet, and the engine fuel consumption is further improved.

According to another aspect of the present invention, there is provided a differential device including an outer differential case which is rotated by 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. A mechanism and an actuator according to any one of claims 1 to 4 are provided, and a clutch of the actuator is arranged between the outer differential case and the inner differential case.

This differential device is a differential device that interrupts the driving force on the input side of the differential mechanism, and is arranged between the axles on the wheel side that is disconnected during two-wheel drive of a four-wheel drive vehicle, and the clutch is engaged. If the vehicle is in the four-wheel drive state, and if the clutch is released, the vehicle becomes 2
Wheel drive state.

Further, since the actuators according to the first to fourth aspects are used, it is possible to obtain the same actions and effects as the configurations according to the first to fourth aspects.

A differential device according to a sixth aspect of the present invention is a differential case that is rotated by receiving a driving force of a prime mover; The actuator according to any one of the aspects is provided, and the clutch of the actuator is arranged between any one of the side gears and a wheel thereof.

This differential device is a differential device in which the driving force is interrupted on the output side of the differential mechanism. Like the differential device of claim 5, the differential device on the side of the wheels that is disconnected during two-wheel drive of a four-wheel drive vehicle. It is placed between the axles, and if the clutch is engaged, the vehicle will be in a four-wheel drive state. If the clutch is disengaged, the driving force will be interrupted by the differential rotation of the differential mechanism, and the vehicle will be in a two-wheel drive state. .

Further, by using the actuators according to the first to fourth aspects, it is possible to obtain the same actions and effects as the configurations according to the first to fourth aspects.

According to another aspect of the present invention, there is provided a differential device, which includes an input side torque transmitting member which is rotated by receiving a driving force of a prime mover.
A differential mechanism for distributing rotation of the input-side torque transmission member to a wheel side via a pair of output-side torque transmission members; and the actuator according to any one of claims 1 to 4, wherein the clutch of the actuator is provided. Is arranged between any of the torque transmission members.

In this differential device, a clutch is arranged between any one of torque transmitting members (differential rotating members) constituting the differential mechanism. If the clutch is connected, the differential of the differential mechanism is limited. If the clutch is disengaged, the differential becomes free.

Further, by using the actuators according to the first to fourth aspects, it is possible to obtain the same actions and effects as those of the first to fourth aspects.

[0036]

DESCRIPTION OF THE PREFERRED EMBODIMENTS [First Embodiment] An actuator 1 and a front differential 3 (differential device) using the same will be described with reference to FIGS.

The actuator 1 has the features of claims 1, 2 and 4, and the front differential 3 has the features of claim 5. FIG. 1 shows the actuator 1 and the front differential 3. The left and right directions are the four-wheel drive vehicle in which the front differential 3 is used and the left and right directions in FIGS. Further, members and the like not given reference numerals in the following description are not shown.

The front differential 3 (differential device for distributing the driving force of the engine to the left and right front wheels) is a differential device having a driving force interrupting function on the input side of the differential mechanism, and is a front axle of a four-wheel drive vehicle. It is placed between the two and cuts the driving force to the front wheels when driving two wheels.

The power transmission system of a four-wheel drive vehicle using the front differential 3 includes an engine (motor), a transmission, a transfer, a 2-4 switching mechanism, a front wheel side propeller shaft, a front differential 3, a front axle, and left and right wheels. It consists of front wheels, rear wheel side propeller shafts, rear differentials (a differential device that distributes engine drive power to the left and right rear wheels), rear axles, left and right rear wheels, and so on.

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

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

The driving force distributed to the rear wheel side is transmitted from the rear wheel side propeller shaft to the rear differential, and distributed from the rear differential to the left and right rear wheels via the rear axle.

The driving force distributed to the front wheels is 2-4 while the 2-4 switching mechanism and the front differential 3 are connected.
It is transmitted from the switching mechanism and the front wheel side propeller shaft to the front differential 3, and is distributed from the front differential 3 to the left and right front wheels via the front axle, so that the vehicle becomes a four-wheel drive state.

2-4 switching mechanism and front differential 3
When the connection is released, the front wheels are disconnected from the engine, and the vehicle enters the two-wheel drive state.

The front diff 3 is arranged inside a diff carrier in which an oil reservoir is formed.

The front diff 3 is composed of an actuator 1, an outer diff case 5, an inner diff case 7, a bevel gear type differential mechanism 9, and the like.

The actuator 1 includes a dog clutch 11 (clutch), a return spring 13, a holding plate 15 (connection holding means: connection releasing means), a rotary ring 17 (connection holding means: connection releasing means), and a pressure plate 19 ( Connection holding means: connection releasing means), hydraulic actuator (piston and cylinder: pressing force source), position switch 21 (sensor), controller and the like.

The inner differential case 7 is rotatably supported on the inner periphery of the outer differential case 5, and the left and right boss portions 23, 25 formed on the outer differential case 5 are supported by the differential carrier 26 via thrust bearings. There is.

A ring gear is fixed to the outer differential case 5 with bolts. The ring gear meshes with the drive pinion gear, and the drive pinion gear is formed integrally with the drive pinion shaft. This drive pinion shaft is connected to a transfer 2-4 switching mechanism via a joint and a front wheel side propeller shaft, and the driving force of the engine is transferred from the transfer and 2-4 switching mechanism to this front wheel power transmission system. Rotate the outer differential case 5.

The bevel gear type differential mechanism 9 is composed of a plurality of pinion shafts 27, the same number of pinion gears 29, left and right output side gears 31, 33 and the like.
The pinion gear 29 is rotatably supported on each pinion shaft 27, and the side gears 31 and 33 mesh with each pinion gear 29 from the left and right.

The tip of each pinion shaft 27 is
The inner differential case 7 is engaged with a plurality of through holes 35 formed at equal intervals in the circumferential direction, and is prevented from coming off by a spring pin 37.

Each boss portion 39, 4 of the side gears 31, 33
1 is a support portion 43, 4 formed on the outer differential case 5.
5, the left and right front axles are splined to the bosses 39 and 41, respectively.

Thrust washers 47 are arranged between the side gears 31 and 33 and the outer differential case 5 to receive the meshing thrust force of the side gears 31 and 33.

A spherical washer portion 49 is formed on the inner periphery of the inner differential case 7 so as to face the back surface of each pinion gear 29, and each spherical washer portion 49 is attached to the pinion gear 2.
The centrifugal force of 9 and the meshing reaction force that the pinion gear 29 receives by meshing with the side gears 31 and 33 are borne.

A clutch ring 51 (clutch member) is arranged inside the outer differential case 5, and is supported by the inner periphery of the outer differential case 5 so as to be axially movable.

The dog clutch 11 is composed of meshing teeth 53 formed at the left end of the clutch ring 51 and meshing teeth 55 formed at the right end of the inner differential case 7.

On the left and right sides of the outer differential case 5, 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 return spring 13 includes the retaining ring 63 mounted on the clutch ring 51 and the outer differential case 5.
And the clutch ring 51 are urged in the disengagement direction (rightward) of the dog clutch 11.

A thrust washer 65 that receives an operating force from the actuator 1 is arranged between the left end portion of the inner differential case 7 and the outer differential case 5, and the inner differential case 7 is axially arranged via the thrust washer 65. It is positioned to the left.

The holding plate 15 is, as shown in FIGS.
Cylindrical base 67, a plurality of sets of arms 6 provided in the axial direction
9, 71, and axial gaps 73 provided at a plurality of locations. As shown in FIG. 1, the holding plate 15 is fixed to the outer periphery of the outer differential case 5 by the base 67.

The arm portions 69, 71 of each set are formed in the base portion 67 at equal intervals in the circumferential direction, and the gaps 73 are formed between the arm portions 69, 71 of each set. Also, as shown in FIGS.
Convex portions 75 and 77 are formed inside 9 and 71, respectively.

As shown in FIGS. 1, 2, and 3, the rotary ring 17 has a base 79 having a substantially disk shape, a plurality of arms 81 formed in the base 79 in the axial direction and provided at equal intervals in the circumferential direction, and the base 7.
It is composed of the abutting arm 83 formed in 9. As shown in FIG. 1, the rotating ring 17 is attached to the outer differential case 5 such that the arms 81 are inside the arms 69 and 71 of the holding plate 15, and the base 79 is the clutch ring of the dog clutch 11. It is in contact with the leg portion 61 of 51.

Further, as shown in FIGS. 2 and 4, at the tip of each arm 81, there is a projection 85 which engages with the projections 75, 77 formed on the arms 69, 71 of the holding plate 15. Each is formed.

As shown in FIGS. 1 and 2, the pressure plate 19 is composed of a disk-shaped base portion 87 and four leg portions 89 formed in the base portion 87 in the axial direction and provided at equal intervals in the circumferential direction. As shown in FIG. 1, each leg portion 89 is engaged with an axial groove 91 formed in the right boss portion 25 of the outer differential case 5.

The pressure plate 19 is connected to the outer differential case 5 so as to be movable in the axial direction by the engagement of the leg portion 89 and the axial groove 91.

As shown in FIGS. 1, 2 and 3, cams 93 (coupling holding means: decoupling means) that mesh with each other are provided on the bases 79 and 87 of the rotary ring 17 and the pressure plate 19.
The cam 93 is operated each time the pressure plate 19 is pressed, and the cam force rotates the rotating ring 17 by a certain angle.

The hydraulic actuator is composed of a piston and a cylinder. These are formed in a ring shape and are coaxially arranged on the right side of the pressure plate 19. The cylinder of the hydraulic actuator is connected to an engine-driven oil pump via a control valve.

The controller drives the oil pump,
The hydraulic pressure is supplied to the hydraulic actuator via the control valve, and the hydraulic pressure is stopped.

When the hydraulic pressure is supplied, the hydraulic actuator pushes the clutch ring 51 to the left via the pressure plate 19 and the rotary ring 17, and when the clutch ring 51 is pushed, the dog clutch 11 meshes with the outer differential case. 5 and the inner differential case 7 are connected to each other to be in a locked state (lower half of FIG. 1).

When the hydraulic pressure supply is stopped, the clutch ring 51 is urged by the urging force of the return spring 13.
Returns to the right, the engagement of the dog clutch 11 is released, and the outer differential case 5 and the inner differential case 7 are separated from each other to be in a free state (the upper half of FIG. 1).

The position switch 21 is attached through the differential carrier 26 as shown in FIG.
The probe 95 is in contact with the abutting arm 83 of the rotating ring 17, and switches the switch ON-OFF in response to the axial movement of the rotating ring 17 (the connecting operation and the disconnecting operation of the dog clutch 11) to set the locked state. The free state is detected and the signal is sent to the controller.

Further, the holding plate 15 and the rotating ring 17
As shown in FIG. 4, when the dog clutch 11 is disengaged to be in a free state, the arms 81 of the rotary ring 17 are attached to the holding plate when the dog clutch 11 is disengaged. 15
It is configured to move to a position corresponding to the gap 73.

From this free state, when the hydraulic actuator presses the pressure plate 19, the dog clutch 11 is engaged and locked, and the cam 93 between the rotary ring 17 and the pressure plate 19 operates to rotate the rotary ring 17. Then, the convex portion 85 of each arm 81 moves to a position where the convex portion 85 of the holding plate 15 is engaged.

At this position, the convex portion 85 is engaged with the convex portion 75 by the urging force of the return spring 13, and the dog clutch 11 is held in the locked state.

The position switch 21 detects this locked state and transmits it to the controller, and the controller stops the oil pump and stops the hydraulic pressure supply to the hydraulic actuator.

When the hydraulic actuator presses the pressure plate 19 from the locked state, the cam 93
Is activated and the rotary ring 17 is further rotated, the convex portion 85 of each arm portion 81 moves to a position corresponding to the gap 73 of the holding plate 15, and the engagement between the convex portion 85 and the convex portion 75 is released. The engagement of the dog clutch 11 is released by the urging force of the return spring 13, and the dog clutch 11 becomes free.

The position switch 21 detects this free state and transmits it to the controller, and the controller stops the oil pump and stops the hydraulic pressure supply to the hydraulic actuator.

Thus, each time the hydraulic actuator presses the pressure plate 19, the cam 93 alternately holds and unlocks the lock state (shifts to the free state), and the position switch 21 controls the state. And the oil pump is stopped.

As described above, the connection / disconnection function (dog clutch 11) of the front differential 3 and the 2-4 switching mechanism are simultaneously operated in connection to switch from the two-wheel drive state to the four-wheel drive state. When switching to the two-wheel drive state, the connection release operation is performed at the same time.

In the four-wheel drive state, as described above, the driving force of the engine is transmitted from the 2-4 switching mechanism to the outer differential case 5 via the front wheel side power transmission system, and the inner differential case 7 via the dog clutch 11. It is driven to rotate. This rotation is distributed from the pinion shaft 27 to the side gears 31 and 33 via the pinion gear 29 and transmitted to the left and right front 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 front wheels during traveling on a rough road, the driving force of the engine is differentially distributed to the left and right front wheels by the rotation of each pinion gear 29.

In the two-wheel drive mode, the inner clutch case 7 is disconnected from the front wheels by the dog clutch 11 to bring it into a free rotation state, and the power transmission system from the 2-4 switching mechanism to the outer differential case 5 causes the driving force of the engine to change. And it is separated from both the front wheels and the rotation, and the rotation stops.

As described above, in the two-wheel drive state in which the rotation of the front wheel side power transmission system from the 2-4 switching mechanism to the outer differential case 5 is stopped, the vibration is reduced and the riding comfort is improved, and the front wheel side power transmission system is improved. The wear is reduced in each part of the engine, and the durability is improved. Further, the load on the engine is reduced by the reduction of the rotational resistance, and the fuel consumption is improved.

The outer differential case 5 has openings 57, 5
In addition to No. 9, spiral oil grooves 97, 99 are formed on the inner peripheries of the bosses 23, 25, respectively, and further, oil grooves 97, 9 are provided in the portion facing the thrust washer 47.
Oil grooves 101 and 103, which communicate with each other, are formed.

Since the openings 57 and 59 are formed on the radially outer portion of the outer differential case 5, they are constantly immersed in the oil in the oil reservoir formed on the differential carrier 26, and the oil is rotated as the outer differential case 5 rotates. Flows in and out.

The oil in the oil sump is scraped up by the rotation of the outer differential case 5 (ring gear),
The oil that has been scraped up flows into the outer differential case 5 through the oil grooves 101 and 103 and the thrust washers 47 and 47 due to the screw pump action of the oil grooves 97 and 99.

The oil that has flowed into the outer differential case 5 in this way is transmitted to the gears 29, 31,
33, meshing parts of the pinion shaft 27 and the pinion gear 29, sliding parts of the outer differential case 5 and the inner differential case 7, sliding parts of the outer differential case 5 and the clutch ring 51, the dog clutch 11 (the meshing teeth 5
3, 55) and the like to lubricate and cool them.

The lower part of the hydraulic actuator is also immersed in the oil sump, and is lubricated and cooled.

In this way, the actuator 1 and the front differential 3 are constituted.

As described above, in the actuator 1 and the front differential 3, the dog clutch 11 is in the locked state (driving force transmission state by the engagement of the holding plate 15 and the rotating ring 17 (the convex portions 75, 77 and the convex portion 85). ).

Therefore, since the oil pump and the hydraulic actuator can be stopped after the dog clutch 11 is locked, the fuel consumption of the engine that drives the oil pump can be prevented from lowering.

Furthermore, the pressure switch provided in the pressure section from the oil pump to the hydraulic actuator is no longer necessary,
The cost is reduced accordingly.

Further, since the pressure plate 19 (dog clutch 11) is simply pressed by the hydraulic actuator, the locked state and the unlocked state (transition to the free state) are alternately performed. No operating means is required for switching between the states, and since the pressing force of the hydraulic actuator is used for switching between these states, it is not necessary to separately provide a driving force source for switching.

Therefore, the actuator 1 and the front differential 3 are so simple in structure and can be implemented at a low cost.

Further, by using the position switch 21, the locked state and the free state of the dog clutch 11 can be detected in real time, so that it is possible to immediately stop the oil pump after locking and shifting to the free state. And the effect of reducing engine fuel consumption is further improved.

[Second Embodiment] An actuator 201 and a front differential 203 (differential device) using the actuator 201 will be described with reference to FIG.

The actuator 201 is defined in claims 1, 3, and 4.
The front differential 203 has the features of claim 5. The front diff 203 is the same as the front diff 3 of the four-wheel drive vehicle using the front diff 3 of the first embodiment.
Is used instead of.

Hereinafter, the differences will be described with reference to the same members and the like as those of the actuator 1 and the front differential 3 of the first embodiment by giving the same reference numerals.

The front differential 203 is the actuator 2
01, outer differential case 5 (counterpart member), inner differential case 7, bevel gear type differential mechanism 9 and the like.
1, engagement grooves 205 and 207 (connection holding means: engagement portion),
Snap ring 209 (connection holding means: engaging member), pressure plate 211 (connection releasing means), cam 21
3 (connection releasing means), a return spring 215, a hydraulic actuator (piston and cylinder), a position switch, a controller and the like.

The engagement grooves 205 and 207 are formed on the outer circumference of the clutch ring 51 of the dog clutch 11 and the inner circumference of the outer differential case 5, respectively.

The snap ring 209 is mounted in the engaging groove 205 of the clutch ring 51 and is given an outward biasing force.

The pressure plate 211 has a retaining ring 2
It is positioned on the leg portion 61 of the clutch ring 51 by 17. In addition, a plurality of cam arms 219 are formed on the pressure plate 211 at equal intervals in the circumferential direction,
Each cam arm 219 is inserted into an axial groove 221 formed on the inner circumference of the outer differential case 5.

The cam 213 is formed at the tip of each cam arm 219 and enters between the snap ring 209 and the engagement groove 207 to release the engagement thereof, as described below.

Similar to the position switch 21 of the first embodiment, the position switch is mounted so as to penetrate the differential carrier 26, and its probe comes into contact with the leg portion 61 of the clutch ring 51, so that the axial direction of the clutch ring 51. The switch is turned on and off according to movement (engagement operation and connection release operation of the dog clutch 11), a lock state and a free state are detected, and the signal is sent to the controller.

The return spring 13 is arranged between the pressure plate 211 and the outer differential case 5, and biases the clutch ring 51 in the disengagement direction (rightward) of the dog clutch 11.

The hydraulic actuator is the clutch ring 51.
While pressing, the pressure plate 211 is moved to the right.

The lower half of FIG. 5 shows the dog clutch 11 (front differential 203) in a locked state, and the upper half shows a free state.

From this free state, the hydraulic actuator moves the clutch ring 51 (pressure plate 211).
When is pressed, the dog clutch 11 is engaged and locked, and as shown in the lower half of FIG. 5, the engaging groove 205 moves to a position facing the engaging groove 207 and the snap ring 209 engages. The lock state is maintained by engaging both the groove 205 and the engaging groove 207. At this time, the tip of each cam arm 219 of the pressure plate 211 (cam 21
3) does not reach the engaging groove 207.

The position switch detects this locked state and transmits it to the controller, and the controller stops the oil pump and stops the hydraulic pressure supply to the hydraulic actuator.

When the hydraulic actuator presses the clutch ring 51 from the locked state, the cam arm 219 of the pressure plate 211 moves, and as described above,
The cam 213 enters between the snap ring 209 and the engagement groove 207 to release these engagements, and then the urging force of the return spring 13 causes the dog clutch 11 to move.
The meshing of is released and it becomes free state.

The position switch detects this free state and transmits it to the controller, and the controller stops the oil pump and stops the hydraulic pressure supply to the hydraulic actuator.

As described above, each time the hydraulic actuator presses the clutch ring 51 (pressure plate 211), the engagement groove 205, 207 and the snap ring 209 hold the locked state and the cam 213 releases the lock state (to the free state). And the position switches transmit their states to the controller to stop the oil pump.

In this way, the actuator 201 and the front differential 203 are constituted.

As described above, in the actuator 201 and the front differential 203, the dog clutch 11 is kept in the locked state (driving force transmission state) by the engagement between the engagement grooves 205 and 207 and the snap ring 209.

Therefore, since the oil pump and the hydraulic actuator can be stopped after the dog clutch 11 is locked, the fuel consumption of the engine for driving the oil pump can be prevented from deteriorating and the pressure switch for detecting the pressure can be provided. It becomes unnecessary and the cost is reduced accordingly.

Further, since the hydraulic actuator is configured to alternately press the clutch ring 51 (dog clutch 11) to hold the locked state and release the lock (shift to the free state), these states No operating means is required for switching between the states, and since the pressing force of the hydraulic actuator is used for switching between these states, it is not necessary to separately provide a driving force source for switching.

Therefore, the actuator 201 and the front differential 203 are simple in structure, and can be implemented at low cost.

Further, by using the position switch, the connected state and the free state of the dog clutch 11 can be detected in real time, so that it is possible to immediately stop the oil pump after locking and shifting to the free state. Therefore, the effect of reducing engine fuel consumption is further improved.

If the actuator of the present invention is arranged in the power transmission system on the side of a wheel that is disconnected when driving two wheels in a four-wheel drive vehicle, for example, the clutch can interrupt the driving force and maintain the locked state. It becomes a coupling that can.

If the actuator of the present invention is arranged on the input side of the driving force as in claim 5 (each embodiment) or arranged on the output side of the driving force as in claim 6, Each of the differential devices is provided with an intermittent driving force function and a lock state holding function.

By disposing the actuator of the present invention between the differential rotation members as in claim 7, a differential device having a differential limiting function by the clutch and a differential limiting state holding function is constituted. It

In addition, in the actuator of the present invention,
The clutch is not limited to the mesh 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.

Further, in the actuator and the differential device of the present invention, the pressing force source is a fluid pressure type actuator (piston and cylinder) which is operated by pump pressure.
Alternatively, an electromagnet or an electric motor may be used.

Further, the differential device according to claims 5 and 6 is not limited to a front differential in a four-wheel drive vehicle.
It can also be used for rear differentials.

[0127]

According to the actuator of the first aspect, since the clutch is held in the connected state by the connection holding means, the pressing force source can be stopped after the clutch is connected. For example, the pressing force source is a pump. In the case of pistons and cylinders that operate with pressure, the fuel efficiency of the engine that drives the pump is improved by stopping the pump, and when the pressing force source is an electromagnet, the battery that excites the electromagnet by stopping the excitation of the electromagnet And the burden on the alternator that charges the battery is reduced, and the fuel efficiency of the engine that drives the alternator is improved.

Further, since the connection holding means and the connection releasing means operate alternately only by pressing the clutch by the pressing force source, there is no need for operating means for switching these, and the pressing force of the pressing force source is used for this switching. Since I used
There is no need to separately provide a driving force source therefor.

Therefore, the structure is simple and the cost can be reduced. The actuator according to claim 2 can obtain the same effect as that of the configuration according to claim 1. The actuator of claim 3 can obtain the same effect as that of the structure of claim 1. The actuator of claim 4 can obtain the same effects as those of the configurations of claims 1 to 3.

Further, since the sensor can detect the connected / disengaged state and the disengaged state of the clutch, the operation of the pressing force source such as the pump or the electromagnet is immediately stopped after the clutch is engaged and disengaged. It becomes possible to further improve the fuel economy of the engine. Since the differential device according to the fifth aspect is configured by using the actuator according to the first to fourth aspects, it is possible to obtain the same effects as those of the configurations according to the first to fourth aspects. Since the differential device according to the sixth aspect is configured by using the actuator according to the first to fourth aspects, it is possible to obtain the same effects as those of the configurations according to the first to fourth aspects. The differential device according to claim 7 is
By using the actuator of claims 1 to 4, it is possible to obtain the same effects as those of the structures of claims 1 to 4.

[Brief description of drawings]

FIG. 1 is a sectional view of a first embodiment.

FIG. 2 is a perspective view of a member forming a part of the first embodiment.

3 is a view on arrow A in FIG. 2. FIG.

FIG. 4 is a development view of members for explaining the lock holding function and the lock releasing function of the first embodiment.

FIG. 5 is a sectional view of a second embodiment.

FIG. 6 is a sectional view of a conventional example.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Actuator 3 Front differential (differential device) 5 Outer differential case (counterpart member) 7 Inner differential case 9 Bevel gear type differential mechanism 11 Dog clutch (clutch) 15 Holding plate (connection holding means: connection releasing means) 17 Rotating ring (connection) Holding means: connection releasing means) 19 Pressure plate (connection holding means: connection releasing means) 21 Position switch (sensor) 51 Clutch ring (clutch member) 93 Cam (connection holding means: connection releasing means) 201 Actuator 203 Differential device 205, 207 Engagement groove (connection holding means: engagement part) 209 Snap ring (connection holding means: engagement member) 211 Pressure plate (connection release means) 213 Cam (connection release means)

Claims (7)

[Claims] 1. An actuator comprising: a clutch having a connected state and a disengaged state in which the connection is released; and a pressing force source for applying a pressing force to the clutch to bring the clutch into a connected state. When a pressing force of the pressing force source is received in a state where the clutch is released, a connection holding unit that holds the clutch in a connected state as the clutch is connected, and the pressing force source in a state where the clutch is connected. And an engagement releasing means for returning the clutch to an engagement releasing state when the pressing force is applied. 2. The invention according to claim 1, wherein a cam that operates by receiving the pressing force of the pressing force source,
An actuator characterized in that the connection holding means and the connection releasing means are alternately switched to respective operating states. 3. The invention according to claim 1, further comprising: a clutch member that receives the pressing force of the pressing force source and moves to connect the clutch, wherein the connection holding means includes the clutch member and When the pressing force of the pressing force source is received in a state where the clutch is disengaged from the engaging portion provided on the mating member, the clutch is engaged to engage the engaging portion. And a disengagement means that disengages the engagement member from the engagement portion when receiving a pressing force of the pressing force source in a state where the clutch is engaged. An actuator having a cam for returning the clutch to a disengaged state. 4. The actuator according to any one of claims 1 to 3, further comprising a sensor for detecting a connection state of the clutch. 5. An outer differential case that is rotated by receiving a driving force of a prime mover, an inner differential case that is relatively rotatably disposed inside the outer differential case, and a differential mechanism that is connected to the inner differential case. The actuator according to any one of claims 1 to 4, wherein the clutch of the actuator is arranged between the outer differential case and the inner differential case. 6. A differential case that rotates by receiving the driving force of a prime mover, a differential mechanism that distributes the rotation of the differential case from a pair of output side gears to a wheel side, and a differential mechanism according to claim 1. An actuator, wherein the clutch of the actuator is arranged between any one of the side gears and its wheel. 7. An input-side torque transmission member that rotates by receiving the driving force of a prime mover, and a differential mechanism that distributes the rotation of the input-side torque transmission member to the wheel side via a pair of output-side torque transmission members. A differential device comprising: the actuator according to any one of claims 1 to 4, wherein a clutch of the actuator is arranged between any of the torque transmission members.