JPH094695A - Differential device - Google Patents

Abstract

(57) [Summary] [Purpose] To simplify the structure of the check valve, and significantly reduce the number of parts, processing man-hours, and cost. [Constitution] Differential case 3 which is rotationally driven by an engine
The differential mechanism 47 disposed inside, the differential limiting clutch 51, and the oil pump 5 driven by receiving differential rotation.
5, a hydraulic actuator 53 that engages the clutch 51 by receiving the oil pressure of the pump 55, and an oil port that alternately becomes a suction hole and a discharge hole as the rotational direction of the pump 55 changes.
Ports 81 and 83 and one of the pump 55 are rotated to one side and the other side to move to each side, open the oil port on the open side to supply hydraulic pressure to the actuator 53, and to close the oil port on the closed side. −
Valve members 73 and 75 for blocking pressure leakage and preventing pressure leakage
And a stopper mechanism for positioning the valve members 73 and 75 at predetermined positions.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential device used in a vehicle.

[0002]

2. Description of the Related Art FIG. 1 is disclosed in Japanese Patent Laid-Open No. 62-253530.
No. 3, a transfer device 201 is described.

In this transfer device 201,
The driving force of the engine input from the input shaft 203 is transmitted to the rear wheel side from the first output shaft 205, and the multi-plate clutch 209, the second output shaft 211 and the chain are connected from the rotating case 207 connected to the input shaft 203. It is transmitted to the front wheel side via the transmission device 213.

The multi-plate clutch 209 is an oil pump 215.
It is fastened by a hydraulic actuator 217 which is supplied with hydraulic pressure from. This oil pump 215 has a second output shaft 2
11 (front wheel side) and the rotary case 207 (rear wheel side) receive differential rotation and are driven.

As shown in FIG. 14, the oil pump 215 is a gear pump having a drive gear 219 and a driven gear 221, and when the rotation direction of the oil pump 215 changes, a pair of oil ports which alternately serve as suction holes and discharge holes are formed. 223, 22
In FIG. 5, four check valves 227 and 22 are provided so that oil is always sent to the hydraulic actuator 217 even if the differential rotation is reversed and the rotation direction of the oil pump 215 changes.
9, 231, 233 are provided.

[0006]

However, in the conventional transfer device 201, as described above, one oil pump 215 has four check valves 227, 229, and four check valves 227, 229.
Since the devices 231 and 233 are required, the device becomes complicated and the number of parts increases. Also, depending on the device, there are those that use multiple sets of oil pumps. In this case, the number of check valves is only required to be multiplied by the number of valves required for each oil pump, 4
The check valve mechanism alone makes the device extremely complicated, increases the number of parts and the number of assembly work steps, and increases the cost.

Therefore, the present invention is a differential device in which a hydraulic actuator for engaging a friction clutch for limiting a differential is operated by a built-in oil pump via a check valve. An object of the present invention is to provide a differential device which is simple, has a low number of parts and an assembling man-hour, is low in cost, and does not hinder the performance of an oil pump by a check valve, and which can obtain a sufficient check function.

[0008]

A differential device according to a first aspect of the present invention is a differential device which is rotationally driven by a driving force of an engine, a differential mechanism arranged in the differential case, and a differential mechanism. A friction clutch for limiting the oil pressure, an oil pump that is driven by the differential rotation of the differential mechanism, and sucks oil from the oil sump, and a hydraulic actuator that presses and engages the friction clutch by receiving the oil pressure from the oil pump. -The two oil ports on the oil sump side that alternately become the suction hole and the discharge hole as the rotation direction of the oil pump changes, and the suction port and the discharge hole alternately as the rotation direction of the oil pump changes. 2 hydraulic actuator side oil ports
When the oil pump reverses to one side and the other side due to the change in the direction of the differential rotation, the oil pump receives the rotation and rotationally moves to the one side and the other side, and the open part becomes the oil reservoir The first valve member that overlaps with the side oil port to open it and closes the oil port on the side of the oil sump where the closed portion becomes the discharge hole, and with the change in the direction of the differential rotation. When the oil pump reverses to one side and the other side, it receives the rotation and rotationally moves to the one side and the other side, and the closed part overlaps with the oil port on the hydraulic actuator side that became the suction hole and closes it. And a second valve member for opening the hydraulic port on the hydraulic actuator side, the opening portion of which serves as a discharge hole, and opening the same, and a stopper mechanism for positioning each valve member at a predetermined position during the movement. It is characterized by having and.

A differential device according to a second aspect of the present invention is the differential device according to the first aspect, wherein the opening portion of the valve member has the same shape as the opening of the oil port and is not smaller than the opening area.

A differential device according to a third aspect of the present invention is the differential device according to the first aspect, wherein the opening portion of the valve member is an elongated hole elongated in the moving direction of the valve member.

In the differential device of the fourth aspect, the valve member is a plate-like member, and as the valve member moves to one side and the other side, it serves as a closing portion that overlaps and closes one oil port, and the other one. 2. The differential device according to claim 1, wherein the overlapping with the oil port is released to form an opening portion for opening the oil port.

According to a fifth aspect of the present invention, in the differential device, the stopper mechanism is provided on one of the fixed side member and the valve member, and on the other side of the fixed side member and the valve member. The differential device according to any one of claims 1 to 4, wherein the differential device comprises a concave portion that is restricted to a range.

A differential device according to a sixth aspect of the present invention is the differential device according to the fifth aspect, wherein the convex portion is a pin provided on the fixed side member and the concave portion is a long hole provided on the valve member so that the pin engages. .

In the differential device according to a seventh aspect, the stopper mechanism includes a convex portion of the fixed member and an end portion of the valve member that abuts on the convex portion to position itself. Differential device.

According to another aspect of the differential apparatus of the present invention, the oil pump is a plurality of sets of external gear pumps having a sun gear arranged coaxially with the differential case and a plurality of pinion gears arranged on the outer periphery of the sun gear. The first and second valve members are arranged across the external gear pump, and one or both of the first and second valve members for each gear pump are integrally formed in a ring shape. Either of the differential devices.

[0016]

In the differential device of each claim, when differential rotation occurs, the oil pump is driven, the hydraulic actuator receives the hydraulic pressure thereof, and the friction clutch is pressed to limit the differential. Since the pump work and oil pressure of the oil pump increase as the differential rotation speed increases, this differential limiting function is speed sensitive.

Two oil ports per pump on the oil sump side of the oil pump and two oil ports per pump on the hydraulic actuator side are:
When the direction of the differential rotation changes and the oil pump reverses, the suction holes and the discharge holes are alternately changed. Valve members are movably arranged between the oil pump and the oil reservoir side oil port and between the oil pump and the hydraulic actuator side oil port, respectively. Upon this movement, each valve member is positioned at a predetermined position by the stopper mechanism.

When the oil pump rotates to one side, these valve members receive the rotation and move to one side. On the oil sump side, the open part of the valve member overlaps and opens the oil port formed as the suction hole, sucks oil from the oil sump, and the closed part of the valve member serves as the discharge port. It overlaps and closes this. On the hydraulic actuator side, the closed portion of the valve member overlaps and closes the oil port which is the suction hole, and the open portion of the valve member overlaps the oil port which is the discharge hole. Open to supply oil pressure to the hydraulic actuator.

Next, when the oil pump rotates to the other side,
Each valve member moves to the other side in response to its rotation, and on both the oil reservoir side and the hydraulic actuator side, the oil port that was the suction hole changed to the discharge hole, and the oil port that was the discharge hole changed. Change to a suction hole.

On the oil sump side, the open portion of the valve member overlaps the oil port which has been changed to the suction hole to open it, sucks oil from the oil sump, and the closed portion of the valve member is changed to the discharge hole. It overlaps with the oil port and closes it. On the hydraulic actuator side, the closed portion of the valve member overlaps and closes the oil port changed to the suction hole, and the open portion of the valve member overlaps the oil port changed to the discharge hole. Open to supply oil pressure to the hydraulic actuator.

As described above, no matter which direction the oil pump rotates, on the oil sump side, the oil port on the suction side is
The oil port on the discharge side is closed while the oil port on the discharge side is closed, and the oil port on the suction side is closed and the oil port on the discharge side is opened on the hydraulic actuator side. Inhaled hydraulic actuator
Supplied to

Thus, regardless of the rotation direction of the oil pump, the check function of each valve member rectifies the flow of oil in one direction, so that oil is always supplied from the oil sump to the hydraulic actuator.

Further, unlike the conventional example in which two (four in total) check valves are required for each oil pump on the oil sump side and the hydraulic actuator side, the valve member is moved to perform the check function. According to the present invention, one (two in total) valve member can be provided on each side to perform the check function. Therefore, in a differential device using a plurality of oil pumps, For example, because it can be made into a ring shape and integrally configured, the number of valve members does not have to be increased to two, and the structure is extremely simple, and the number of parts, assembly work and processing man-hours are greatly reduced, and the cost is greatly reduced. To be done.

A differential device according to a second aspect is the differential device according to the first aspect, wherein the opening portion of the valve member has the same shape (for example, a round hole) as the opening of the oil port and has the same area as the opening. The differential device according to claim 3 is the differential device according to claim 1, wherein in the differential device according to claim 1, the opening portion of the valve member is an elongated hole formed in the moving direction of the valve member. The differential device of 4 is
The differential device according to claim 1, wherein the valve member is a plate-like member, and the valve member serves as a closing portion that overlaps with one oil port and closes the oil port as the valve member moves to one side and the other side.
The other oil port is configured so that the overlap with the other oil port is released to open the oil port, and both have the same effect as the differential device of the first aspect.

In addition to this, in the differential device of the second aspect, since the opening of the valve member has the same shape as the opening of the oil port and is not narrower than that, the oil port is completely opened at the time of opening, and the oil The oil pump exerts sufficient performance without blocking the flow. Further, in the differential device according to the third aspect, the movement distance of the valve member is shortened by making the opening portion a long hole, and the durability of the valve member is improved accordingly. Further, in the differential device according to the fourth aspect, since the check function is performed by overlapping and releasing the overlap between the valve member and the oil port due to the movement of the valve member, the valve member can be a plate member having a simple shape. It will be possible, and the cost will be lower. Since the check function is performed by moving only the plate-shaped valve member, the valve member with a small inertia can move instantly according to the rotation direction of the oil pump with respect to the oil port of the fixed side member. The fluidity of the suctioned and discharged oil is good and the response of the actuator, that is, the response of the differential limiting force by the friction clutch is excellent.

A differential device according to a fifth aspect is the differential device according to any one of the first to fourth aspects, wherein a stopper mechanism is provided on one of the fixed side member and the valve member, and the fixed side member and the valve member. The differential device according to claim 6 is constituted by a concave part provided on the other side, and the movement of the convex part is restricted by the concave part within a predetermined range. In this configuration, the pin provided on the above is a convex portion, and the long hole of the valve member with which this pin engages is a concave portion. The differential device according to claim 7 is the differential device according to claim 1.
In the differential device of any one of to
The stopper mechanism is composed of a convex portion of the fixed member and an end portion of the valve member that abuts on the convex portion to position itself.

In any case, the valve member is accurately positioned by these stopper mechanisms, and the same effect as the differential device according to any one of claims 1 to 4 can be obtained.

A differential device according to claim 8 is the differential device according to any one of claims 1 to 7, wherein a plurality of sun gears are provided coaxially with the differential case and a plurality of pinion gears are provided on the outer periphery of the sun gear. An oil pump is configured with a set of external gear pumps, and one or both of the first and second valve members for each gear pump are integrally formed in a ring shape to integrate the check valve function of each gear pump. The same effect as the differential device according to any one of claims 1 to 7 is obtained.

In addition to this, for example, 4 per oil pump
Unlike the conventional example where 16 check valves are required in the example where 4 check valves are required and 4 sets of oil pumps are used, the number of valve members is 2 even if multiple sets of oil pumps are used. Therefore, the structure is extremely simple, the number of parts, the number of assembling work and the number of working are greatly reduced, and the cost is significantly reduced.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. This embodiment has the features of claims 1, 2, 4, 5, and 8. FIG. 1 shows a differential device 1 of this embodiment. Note that the left and right directions are the left and right directions in FIG. 1, and the members and the like without reference numerals are not shown.

As shown in FIG. 1, the differential case 3 of the differential device 1 is constructed by fixing a casing body 5 and a cover 7 with bolts 9. The differential case 3 is arranged inside the differential carrier, and an oil reservoir is formed in the differential carrier.

The left and right boss portions 11 and 13 of the differential case 3 are supported by the differential carrier via bearings. A ring gear is fixed to the differential case 3 with bolts, and the ring gear meshes with the drive gear of the drive force transmission system.
Thus, the differential case 3 is rotationally driven by the driving force of the engine via the transmission and the driving force transmission system.

As shown in FIG. 1, inside the differential case 3,
A plurality of pinion shafts 17 centering around the boss portion 15
Are radially arranged, and the outer ends of the pinion shafts 17 are supported in the grooves 19 of the differential case 3. A pinion gear 21 is rotatably supported on each pinion shaft 17.

Inside the differential case 3, left and right side gears 23 and 25 are arranged. Each side gear 23,
25 is welded to bosses 27 and 29, respectively. These side gears 23, 25 are supported from the outside in the radial direction by meshing with the pinion gear 21. A spherical washer 31 is arranged between the pinion gear 21 and the differential case 3, and bears the centrifugal force of the pinion gear 21 and the meshing reaction force received by the pinion gear 21 by meshing with the side gears 23 and 25.

The boss 27 of the left side gear 23 is rotatably supported by the bearing 33 of the differential case 3 and the inner periphery of the boss 37 of the pump cover 35, which will be described later, and the boss 29 of the right side gear 25 is the bearing of the differential case 3. It is rotatably supported by the portion 39. A washer 41 is arranged between the left side gear 23 and the pump cover 35, and a washer 43 is arranged between the right side gear 25 and the differential case 3. The side gears 23 and 25 are spline-connected to the axle (output shaft) via the bosses 27 and 29, and are positioned by the retaining rings 45 and 45.

In this way, the bevel gear type differential mechanism 47 is constructed. Pinion shaft 17 of differential mechanism 47
The pinion gear 21 and the side gears 23 and 25 are appropriately movable in the axial direction between the pinion shaft 17 and the groove 19.

The driving force of the engine for rotating the differential case 3 is distributed from the pinion shaft 17 to the side gears 23 and 25 via the pinion gear 21, and is transmitted to the wheel side via each axle. Further, for example, when a driving resistance difference occurs between the wheels during traveling on a rough road, the driving force of the engine is differentially distributed to the left and right sides by the rotation of each pinion gear 21.

The top 49 of the left side gear 23 and the differential gear
A multi-plate clutch 51 (friction clutch) is arranged between the clutch 3 and the clutch 3. A hydraulic actuator 53 is arranged on the left side of the hydraulic actuator 53, and four sets of external gear pumps 55 (oil pumps) are arranged on the left side of the hydraulic actuator 53.

A back ring 57 is arranged between the multi-plate clutch 51 and the differential case 3 to bear the pressing force of the multi-plate clutch 51.

The piston 59 of the hydraulic actuator 53 is arranged between the outer periphery of the boss portion 37 of the pump cover 35 and the inner periphery of the differential casing 3 so as to be axially movable via seals 61 and 63, respectively. There is. Also, the hydraulic actuator 53
The cylinder 65 is formed between the piston 59, the pump cover 35, and the differential case 3.

Each gear pump 55 includes a pump cover 35, a pump body 67, a sun gear 69, and four pinion gears 7.
1, a washer 73 (a ring-shaped first valve member of a plate member) shown in FIG. 2, and another washer 75 (a ring-shaped second valve member of a plate member) and the like.
The washers 73, 75 are arranged on the left and right in the rotation axis direction of the differential case 3 with the gear pump 67 interposed therebetween.

The outer periphery of the pump body 67 is positioned on the differential casing 3, and is fixed to the differential casing 3 together with the pump cover 35 by bolts 76. The pump body 67 is provided with large and small storage holes 77, 79.
Four nines are formed outside the storage hole 77 at equal intervals in the circumferential direction. The storage holes 77 and 79 communicate with each other to form a pump chamber. The sun gear 69 and the pinion gears 71 are slidably and rotatably housed in the housing holes 77 and 79, respectively, and are meshed with each other in the pump chamber to form four sets of gear pumps 55.
Is composed.

The inner circumference of the sun gear 69 is splined to the outer circumference of the boss 27 of the left side gear 23. Therefore, when differential rotation occurs in the differential mechanism 47, the pinion gear on the side of the pump body 67 fixed to the differential case 3 is fixed. 71 and the sun gear 69 on the left side gear 23 side rotate relative to each other.
The pair of gear pumps 55 operates.

As shown in FIGS. 3, 4, and 5, the cover 7 of the differential case 3 has an oil port 81 corresponding to one circumferential direction side of the meshing portion of the sun gear 69 and each pinion gear 71 and the other circumferential direction side. Corresponding to the oil port 83. Further, the pump cover 35 is provided with an oil port 85 corresponding to one side in the circumferential direction of the meshing portion of the gears 69 and 71 and another oil port corresponding to the other side in the circumferential direction. These oil ports are round holes.

As shown in FIG. 1, an oil pocket 87 (oil reservoir) is fixed to the outside of the cover 7 of the differential case 3. The oil pocket 87 is composed of a ring member 89 and an elastic member 91, and forms an oil reservoir with the cover 7. The oil sump is made liquid-tight by the elastic member 91. A sliding ring 93 is slidably connected to the ring member 89, and the sliding ring 93
Is fixed to the differential carrier side.

A circumferential groove is provided in one of the sliding ring 93 and the oil pocket 87, and an oil hole is provided in the other. Even if the sliding ring 93 and the oil pocket 87 rotate relative to each other, the circumferential groove and the oil hole are always in communication with each other, thus forming an oil connector between the sliding ring 93 and the oil pocket 87. Has been done.

An oil pipe is connected to the sliding ring 93, and this oil pipe communicates with the oil reservoir of the differential carrier via an oil strainer and a control valve. An air pipe for mixing air with oil is connected to the control valve via a flow rate adjusting valve. The control of these control valve and flow rate adjusting valve is performed by the controller.

The oil or the mixture of oil and air is thus supplied to the oil pocket 87, and the oil ports 81 and 83 are always immersed in them.

As shown in FIG. 2, the washer 73 (first valve member) is provided with four round holes 95 (opening portions having the same shape as the opening of each oil port) and a closing portion 97 in the circumferential direction. It is a ring-shaped plate material. Further, the washer 75 (second valve member) is also a ring-shaped plate member provided with four round holes (open portions having the same shape as the openings of the oil ports) and closed portions in the circumferential direction.

As shown in FIGS. 4 and 5, the round hole 95 of the washer 73 has a diameter slightly larger than the oil ports 81 and 83 of the cover 7. Also, the round hole of the washer 75 is made slightly larger than each oil port of the pump cover 35.

As shown in FIG. 3, the cover 7 (fixed member) is provided with a groove 99 in which a washer 73 is slidably and rotatably housed.
Is provided. Claw 101 is provided on the outer periphery of the washer 73.
(Convex portion) is provided, and when the washer 73 is rotated, the claw 101 abuts on the groove 99, and the contact portion 103, 1
A notch 107 (recess) having 05 is provided to form a stopper mechanism.

Further, the pump cover 35 (fixed member) is provided with a groove 109 for accommodating the washer 75 in a slidable and rotatable manner. A claw (convex portion) is provided on the outer periphery of the washer 75, and a notch (concave portion) having an abutting portion against which the claw abuts when the washer 75 rotates is provided in the groove 109, which constitutes a stopper mechanism. .

Each of the washers 73 and 75 rotates in the rotational direction due to friction between the sun gear 69 and the pinion gear 71 as the gear pump 55 reverses (differential rotation reverses). For example, in the washer 73, as shown in FIG. The claw 101 rotationally moves between a position where the claw 101 abuts against the abutting portion 103 and a position where the claw 101 abuts against the abutting portion 105 as shown in FIG. In this way, each washer 73, 75 is positioned at a predetermined position by each stopper mechanism as it moves.

Arrows 110 and 111 in FIGS. 4 and 5 indicate the rotation directions of the sun gear 69 when viewed from the right.

As shown in FIG. 4, when the gear pump 55 operates and the sun gear 69 rotates clockwise as indicated by arrow 110, the oil port 81 becomes the suction side on the oil pocket 87 side, and the oil port 83 becomes the oil port 83. It is on the discharge side. or,
On the hydraulic actuator 53 side, the oil port in the direction of arrow 110 is the suction side, and the oil port in the direction opposite to arrow 110 is the discharge side.

At this time, on the oil pocket 87 side, the rotation of the washer 73 causes the oil port 8 on the suction side to move.
1 is opened by overlapping with the round hole 95, and is in a state of sucking oil from the oil pocket 87 as shown in (1-1) of FIG. 6, and the oil port 83 on the discharge side overlaps with the closing portion 97 and is closed. Each gear pump 5 as shown in (2-1) of FIG.
The pressure leakage from 5 is prevented.

On the hydraulic actuator 53 side, the rotation of the washer 75 causes the oil port on the discharge side to be opened by overlapping the round hole, so that oil is supplied to the hydraulic actuator 53 and the oil port on the suction side is opened. Is closed and overlapped with the closed portion, so that pressure leakage from the hydraulic actuator 53 is prevented.

Further, as shown in FIG. 5, when the gear pump 55 is reversed and the sun gear 69 rotates counterclockwise as indicated by the arrow 111, the oil port 83 changes to the suction side on the oil pocket 87 side, and the oil port 83 changes. 81 changes to the discharge side. On the hydraulic actuator 53 side, the oil port in the direction of arrow 111 is the suction side, and the oil port in the direction opposite to arrow 111 is the discharge side.

At this time, on the oil pocket 87 side, the rotational movement of the washer 73 causes the oil port 83 on the suction side.
Is opened by overlapping with the round hole 95, and the oil is sucked from the oil pocket 87 as shown in (2-2) of FIG. 6, and the oil port 81 on the discharge side overlaps with the closing portion 97 and is closed. Each gear pump 55 as shown in (1-2) of 6
The condition to prevent pressure leakage from

On the hydraulic actuator 53 side, the rotation of the washer 75 causes the oil port on the discharge side to be opened by overlapping the round hole, so that oil is supplied to the hydraulic actuator 53 and the oil port on the suction side is opened. Is closed and overlapped with the closed portion, so that pressure leakage from the hydraulic actuator 53 is prevented.

Thus, even if the gear pump 55 rotates in any direction (in which direction the differential rotation occurs),
The check function of each washer 73, 75 rectifies the flow of oil in one direction, so that the oil is constantly sucked from the oil pocket 87, and the hydraulic actuator 5 is used when necessary.
3.

Cylinder 65 of hydraulic actuator 53
When oil pressure is supplied to the hydraulic actuator 53, the hydraulic actuator 53 presses the multi-plate clutch 51 via the piston 59 to engage it. At this time, the rotation of the side gear 23 is braked by the pump work of each gear pump 55 and the frictional resistance of the multi-plate clutch 51, and the differential of the differential mechanism 47 is limited. Since the pump work and discharge pressure of each gear pump 55 increase as the differential rotation speed increases, this differential limiting function is a differential rotation speed sensitive type.

The piston 59 is provided with an orifice 113 to discharge air mixed in the oil while the hydraulic pressure is being applied to the cylinder-65, and to appropriately discharge the oil. The discharged oil lubricates the multi-plate clutch 51, the meshing portion of each gear, the sliding portion between the pinion gear 21, the pinion shaft 17, and the spherical washer 31, and the like,
It is discharged to the outside by centrifugal force from the openings 115 and 117 provided in the differential case 3, and returns to the oil reservoir of the differential carrier.

As described above, the controller for controlling the control valve and the flow rate adjusting valve provided in the oil flow path to the oil pocket 87 includes a vehicle speed sensor, a brake sensor, a steering angle sensor, and the like. Is sent.

The controller controls the control valve based on these signals. For example, the running speed of the vehicle is 40 km / h.
In the following cases, the air is shut off to allow the oil to flow, and the air is mixed with the oil when the traveling speed exceeds 40 km /, the brake is applied, or the steering angle exceeds the set value. When the flow rate adjusting valve is adjusted while air is flowing, the amount of air mixed into the oil is adjusted.

When the air is shut off, only oil is supplied to each gear pump 55, and the differential limiting force rapidly increases as the differential rotation speed increases. Further, when air is mixed with oil, the discharge pressure of each gear pump 55 is lowered, so that the engagement force of the multi-plate clutch 51 is reduced and the increase of the differential limiting force is suppressed to be low. Furthermore, various differential limiting characteristics can be obtained by adjusting the flow rate adjusting valve while mixing air.

Thus, the differential device 1 is constructed.

As described above, in the differential device 1, the hydraulic actuator 5 sucks oil from the oil pocket 87 by the check function of the washers 73 and 75 that move to one side and the other side by reversing the gear pump 55.
3 and the pressure leakage is prevented, the operating pressure of the hydraulic actuator 53 is always obtained regardless of the differential rotation direction, and the differential limiting force is obtained.

Even in the case where four sets (a plurality of sets) of gear pumps 55 are used as in the differential device 1, since the valve member can be formed in a ring shape and integrally formed like washers 73 and 75, four sets of oils can be used. Unlike the conventional example where 16 check valves were required when using a pump, only two valve members, washers 73 and 75, are required.
The structure is extremely simple, and the number of parts, the number of assembly work steps, and the cost are significantly reduced.

Further, since the washer 73, 75 is configured to be moved to perform the check function, the washer having a small inertia can be instantly moved with respect to the oil port of the fixed member according to the rotation direction of the oil pump. ,
Therefore, the fluidity of the oil sucked and discharged from the oil pump is good, and the response of the actuator, that is, the response of the differential limiting force by the friction clutch is excellent.

Therefore, in the vehicle using the differential device 1, the stable speed-sensitive differential limiting function prevents the drive wheels from idling on a bad road or the like, and the drivability is improved.
Further, in a sharp turn that causes a large differential rotation speed, or an S-shaped running in which the turning direction changes, the attitude and behavior of the vehicle are stabilized by the differential limiting function of the differential device 1 that has a fast response to the differential rotation. During gentle turning with a small differential rotation speed, the differential limiting force is relaxed, and smooth and stable turning travel is possible.

Next, FIGS. 7, 8, 9, 10, 11 and 1.
Another embodiment of the valve member and the stopper mechanism used in the differential device of the present invention will be described with reference to FIG. Hereinafter, members having the same functions as those in the first embodiment will be referred to by the same reference numerals, and the description of these members having the same functions will be omitted to avoid duplication. Each of the following embodiments will be described by taking a valve member disposed on the cover 7 side (oil pocket 87 side) of the differential case 3 as an example.

7 and 8 show a second embodiment, which has the features of claims 1, 3, 4, 6, and 8.

As shown in FIG. 7, the washer 119 (ring-shaped valve member) on the oil pocket 87 side used in this embodiment is provided with four elongated holes 121 (opening portions) and both sides thereof. It is a ring-shaped plate member having four closed portions 123 and 125 in the circumferential direction. Further, as shown in FIG. 8, the cover 7 is provided with a groove 127 in which the washer 119 is slidably and rotatably accommodated. The long hole 121 of the washer 119 is wider than the oil ports 81 and 83 of the cover 7. Further, a pin 129 (projection) is embedded in the groove 127 of the cover 7, and the washer 119 is provided with a long hole 131 which engages with the pin 129 and constitutes a stopper mechanism.
(Concave portion) is provided.

The washer 119 rotates in these rotational directions due to friction with the sun gear 69 and the pinion gear 71 as the gear pump 55 reverses (differential rotation reverses).
The pin 129 is rotationally moved between a position where the pin 129 abuts the abutting portion 133 of the long hole 131 and a position where the pin 129 abuts the abutting portion 135.

The washer (ring-shaped valve member) on the side of the hydraulic actuator 53 has the same shape as the washer 119, and is slidably and rotatably housed in a groove formed in the pump cover 35. This washer is also a pump cover 35
By a stopper mechanism provided between and, it is positioned at a predetermined position during movement.

The rotation of the gear pump 55 causes the washer 1 to move.
When 19 rotates and the pin 129 abuts on the abutting portion 133, the long hole 121 overlaps with the oil port 81 on the suction side, oil is sucked from the oil pocket 87, and the closing portion 123 becomes the discharge side. Oil port 83
To prevent pressure leakage. On the side of the hydraulic actuator 53, the other washer rotates to prevent the pressure leak from overlapping the oil port on the suction side and the closed portion, and prevent the oil port on the discharge side and the long hole. Overlap and supply oil pressure to the hydraulic actuator 53.

Further, the gear pump 55 is reversed and the pin 129
Washer 11 up to the position where
When 9 rotates, this time, the oil port 83 on the suction side overlaps with the elongated hole 121, the oil is sucked from the oil pocket 87, and the closing portion 123 overlaps with the oil port 81 on the discharge side. Prevent pressure leaks. On the side of the hydraulic actuator 53, the other washer rotates to prevent the pressure leak from overlapping the oil port on the suction side and the closed portion, and prevent the oil port on the discharge side and the long hole. Overlap and supply oil pressure to the hydraulic actuator 53.

Thus, even if the gear pump 55 rotates in any direction (in which direction the differential rotation occurs),
The check function of each washer rectifies the flow of oil in one direction, the oil is constantly sucked from the oil pocket 87, and is supplied to the hydraulic actuator 53 when necessary to press the multi-plate clutch 51 and each gear pump 55. It is possible to limit the differential of the differential mechanism 47 by the pump work and the frictional resistance of the multi-plate clutch 51.

Since the washer is moved to perform the check function, the washer having a small inertia can be instantly moved to the oil port of the fixed member according to the rotation direction of the oil pump. The suction and discharge oils of the pump have good fluidity, and the operation response of the actuator, that is, the response of the differential limiting force by the friction clutch is excellent.

In addition to this, even if four sets of gear pumps 55 are used as in the first embodiment, the check function of each gear pump 55 can be performed by the washer 119 and the other washers, respectively. Unlike the above, the structure is extremely simple, and the number of parts and the cost are greatly reduced.

Also, unlike the conventional example in which the washer 239, 247 obstructs the oil flow, in the differential device of this embodiment, the open side oil port is completely opened by the elongated hole and the closed side oil port. Since the gear is completely closed by the closing portion, each gear pump 55 can exhibit sufficient performance, oil leakage is prevented, and the check function is sufficiently performed.

Therefore, this differential device can obtain a differential limiting function with a fast response to differential rotation,
A large differential limiting force corresponding to the capacity of each gear pump 55 is obtained, and the differential limiting function is stabilized by the stable oil flow.

Further, by making the open portion a long hole, the rotational movement distance of each washer is shortened accordingly, so that the durability of each washer is improved.

9 and 10 show a third embodiment, which has the features of claims 1, 3, 7, and 8.

As shown in FIG. 9, the washer 137 (ring-shaped valve member) on the oil pocket 87 side used in this embodiment is provided with four elongated holes 139 (opening portions) and both sides thereof. It is a ring-shaped plate material having four closed portions 141 and 143 in the circumferential direction. Further, as shown in FIG. 10, the cover 7 is provided with a groove 145 in which the washer 137 is slidably and rotatably accommodated. The long hole 139 of the washer 137 is wider than the oil ports 81 and 83 of the cover 7. In addition, the block 14 is provided in the groove 145 of the cover 7.
7 (convex portion) is fixed, and the washer 137 is provided with a notch 149. Each end 151, 153 of the cutout 149 constitutes a stopper mechanism that abuts on the block 147.

The washer 137 rotates in the rotational directions of the sun gear 69 and the pinion gear 71 due to friction with the inversion of the gear pump 55 (inversion of differential rotation).
The respective end portions 151 and 153 are rotationally moved between positions where the respective end portions 151 and 153 abut the block 147.

The washer (ring-shaped valve member) on the side of the hydraulic actuator 53 has the same shape as the washer 137 and is slidably and rotatably housed in the groove formed in the pump cover 35. This washer is also a pump cover 35
By a stopper mechanism provided between and, it is positioned at a predetermined position during movement.

When the washer 137 rotates to a position where the end 151 abuts against the block 147, the long hole 139 overlaps with the oil port 81 on the suction side, sucks oil from the oil pocket 87, and discharges the block 141. Overlapping with the oil port 83 on the side prevents pressure leakage. On the side of the hydraulic actuator 53, the other washer rotates to prevent the pressure leak from overlapping the oil port on the suction side and the closed portion, and prevent the oil port on the discharge side and the long hole. Overlap and supply oil pressure to the hydraulic actuator 53.

Further, the gear pump 55 is reversed and the end portion 153
Washer 137 until it hits block 147
When is rotated, this time, the long hole 139 overlaps with the oil port 83 on the suction side, the oil is sucked from the oil pocket 87, and the closing portion 143 overlaps with the oil port 81 on the discharge side. Block. On the side of the hydraulic actuator 53, the other washer rotates to prevent the pressure leak from overlapping the oil port on the suction side and the closed portion, and prevent the oil port on the discharge side and the long hole. Overlap and supply oil pressure to the hydraulic actuator 53.

Thus, even if the gear pump 55 rotates in any direction (in which direction differential rotation occurs),
The check function of each washer rectifies the flow of oil in one direction, the oil is constantly sucked from the oil pocket 87, and is supplied to the hydraulic actuator 53 when necessary to press the multi-plate clutch 51 and each gear pump 55. It is possible to limit the differential of the differential mechanism 47 by the pump work and the frictional resistance of the multi-plate clutch 51.

In addition to this, as in each of the above-mentioned embodiments, 4
Even if a pair of gear pumps 55 are used, the check function of each gear pump 55 can be performed by the washer 137 and the other washers one by one. Therefore, unlike the conventional example, the structure is extremely simple and the number of parts and cost are reduced. Significantly reduced.

Since the washer is moved to perform the check function, the washer having a small inertia can be instantly moved to the oil port of the fixed member according to the rotation direction of the oil pump. The suction and discharge oils of the pump have good fluidity, and the operation response of the actuator, that is, the response of the differential limiting force by the friction clutch is excellent.

The oil port on the open side is completely opened by the long hole 139, and the oil port on the closed side is completely closed by the closed portions 141 and 143, so that the check function is sufficiently fulfilled. The gear pump 55 can exhibit sufficient performance.

In this way, the differential device of this embodiment can obtain a differential limiting function with a fast response to differential rotation, obtain a large differential limiting force commensurate with the capacity of each gear pump 55, and provide a stable oil flow. This stabilizes the differential limiting function.

Further, since the opening 139 has the elongated hole 139, the rotational movement distance of the washer 137 is shortened accordingly, so that the durability of the washer 137 is improved.

11 and 12 show a fourth embodiment, which has the features of claims 1, 2, 4, 7, and 8.

As shown in FIG. 11, a washer 155 (ring-shaped valve member) used in this embodiment has three round holes 157 (opening portions) and a closing portion 15 provided at two positions.
9 is a ring-shaped plate material including 9 and valve portions 161 and 163. Further, as shown in FIG. 12, the cover 7 is provided with a groove 165 in which the washer 155 is slidably and rotatably accommodated. The round hole 157 of the washer 155 has a larger diameter than the oil ports 81 and 83 of the cover 7. Also, cover 7
The groove 165 is provided with a convex portion 167, and the washer 155 is provided with a notch 169. Each of the ends 171 and 173 of the cutout 169 constitutes a stopper mechanism that abuts against the protrusion 167.

The washer 155 rotates in the rotational direction due to friction between the sun gear 69 and the pinion gear 71 as the gear pump 55 reverses (differential rotation reverses).
The respective end portions 171 and 173 are rotationally moved between positions where the respective end portions 171 and 173 abut the convex portion 167.

The washer (ring-shaped valve member) on the hydraulic actuator 53 side has the same shape as the washer 155, and is slidably and rotatably housed in the groove provided in the pump cover 35. This washer is also a pump cover 35
By a stopper mechanism provided between and, it is positioned at a predetermined position during movement.

When the washer 155 rotates to a position where the end 171 abuts the convex 167, the oil port 83 on the suction side overlaps with the round hole 157, and the valve 16
1 moves to open the oil port 83 of the arrow 175, sucks oil from the oil pocket 87, and
The oil port 81 on the discharge side overlaps with the closing portion 159 to be closed, and the oil port 81 indicated by arrows 177 and 179 overlaps with the moved valve portions 163 and 161 to prevent leakage. Also, hydraulic actuator
On the side of the switch 53, the other washer rotates and the washer 155
Similarly, the oil port on the opening side is opened to supply oil pressure to the hydraulic actuator 53, and the oil port on the closing side is opened.
Block the door.

When the washer 155 rotates to a position where the end 173 abuts the convex 167, the oil port 81 on the suction side overlaps with the round hole 157 this time, and the valve 163 moves further to move the arrow. 177 oil port 8
1 is opened, oil is sucked from the oil pocket 87, and the oil port 83 on the discharge side is closed.
The valve parts 161 and 1 in which the oil port 83 indicated by the arrows 175 and 181 moves, respectively, are blocked by overlapping 59.
It is blocked by overlapping 63 and prevents pressure leakage. On the hydraulic actuator 53 side, the other washer rotates, and like the washer 155, the oil port on the open side is opened to supply the oil pressure to the hydraulic actuator 53, and the oil port on the closed side is closed. Block the door.

Thus, even if the gear pump 55 rotates in any direction (in which direction differential rotation occurs),
The check function of each washer rectifies the flow of oil in one direction, the oil is constantly sucked from the oil pocket 87, and is supplied to the hydraulic actuator 53 when necessary to press the multi-plate clutch 51 and each gear pump 55. It is possible to limit the differential of the differential mechanism 47 by the pump work and the frictional resistance of the multi-plate clutch 51.

In addition to this, in the same manner as in each of the above embodiments, 4
Even if a pair of gear pumps 55 are used, the check function of each gear pump 55 can be performed by using the washer 155 and the other washers one by one. Therefore, unlike the conventional example, the structure is extremely simple and the number of parts and cost are reduced. Significantly reduced.

The oil port on the open side is completely opened by the movement of the round hole 157 and the valve portions 161, 163, and the oil port on the closed side is moved by the movement of the closing portion 159 and the valve portions 161, 163. Since it is completely blocked and the check function is sufficiently fulfilled, each gear pump 55
Can show sufficient performance.

Further, since the washer is configured so as to perform the check function, the washer having a small inertia can be instantly moved in accordance with the rotation direction of the oil pump with respect to the oil port of the fixed side member. The suction and discharge oils of the pump have good fluidity, and the operation response of the actuator, that is, the response of the differential limiting force by the friction clutch is excellent.

In this way, this differential device has a differential limiting function with a fast response to differential rotation, a large differential limiting force corresponding to the capacity of each gear pump 55 is obtained, and a differential oil is provided by a stable oil flow. The limiting function is stable.

Further, the valve parts 161 and 163 are plate-shaped pieces having a simple shape and are low in cost.

Although the oil reservoir for the oil pump is arranged in the differential carrier (outside the differential case) in each embodiment, the oil reservoir may be provided inside the differential case.

In the present invention, the differential mechanism is not limited to the bevel gear type, and for example, the difference in obtaining the torque sensitive differential limiting function is utilized by utilizing the tooth surface frictional resistance of the gear or the frictional resistance between the gear and the differential case. It may be a dynamic mechanism. By using such a differential mechanism, it is possible to obtain a differential device having not only the torque sensitive differential limiting function but also the speed sensitive differential limiting function by the friction clutch and the oil pump as described above.

Further, the friction clutch is not limited to the multi-disc clutch, but may be a cone clutch, for example.

The differential device of the present invention is a differential that distributes the front diff (front wheel side axle diff), the rear diff (rear wheel side axle diff), and the center diff (engine driving force to the front and rear wheels). Device).

[0113]

In the differential device of each claim, the oil pump is driven by the differential rotation to operate the hydraulic actuator, and the friction clutch is pressed to limit the differential.

Therefore, in the differential device according to each of the claims, the oil reservoir side of the oil pump and the hydraulic actuator.
The valve members placed on the oil side and the valve side are moved to one side and the other side by the rotation of the oil pump and positioned at a predetermined position by the stopper mechanism, so that the oil sump is always kept regardless of the rotation direction of the oil pump. This oil can be supplied to the hydraulic actuator.

As described above, the check function can be performed by each one valve member arranged on the oil sump side and the hydraulic actuator side. Further, even if a plurality of sets of oil pumps are used, unlike the conventional example, it is sufficient to use one valve member on each side by integrally forming them. Therefore, the structure is extremely simple, and the number of parts and the cost are greatly reduced.

In addition to this, since the pin for fixing the valve member and the countersinking for the valve member are not required, the number of parts and the work for fixing the valve member with the pin and the countersinking are greatly reduced. , The cost is greatly reduced.

Further, unlike the conventional example, in the present invention, the oil port on the opening side is completely opened by the movement of the valve member, so that the oil pump can exhibit sufficient performance and the discharge pressure of the oil pump. Even when is small, the check function is perfect and pressure leakage can be prevented.

The differential device according to a second aspect of the present invention is such that the opening portion of the valve member has the same shape as the opening of the oil port and has the same area as or wider than the opening. According to the differential device of claim 4, the opening portion of the valve member is formed into a long hole formed in the moving direction of the valve member. With the movement of the oil port, one oil port is overlapped with the oil port to close the oil port, and the other oil port is released from the overlap with the oil port to open the oil port. Also obtains the same effect as the differential device of claim 1.

In addition to this, in the differential device of the second aspect, since the opening of the valve member has the same shape as the opening of the oil port and is not narrower than that, the oil flow of the oil port is not obstructed and the oil pump Shows sufficient performance. Further, in the differential device according to the third aspect, the movement distance of the valve member is shortened by making the opening portion a long hole, and the durability of the valve member is improved accordingly.
Further, in the differential device according to the fourth aspect, since the check function is performed by overlapping and releasing the overlap between the oil port and the valve member due to the movement of the valve member, the valve member can be a plate-shaped member having a simple shape. Becomes possible,
That makes it lower cost.

Further, since the check function is performed by moving only the plate-shaped valve member, the washer having a small inertia can be moved instantaneously in accordance with the rotation direction of the oil pump with respect to the oil port of the fixed member. is there,
Therefore, the fluidity of the oil sucked in and discharged from the oil pump is good, and the operation response of the actuator, that is, the response of the differential limiting force by the friction clutch is excellent.

A differential device according to a fifth aspect of the present invention is the differential device according to any one of the first to fourth aspects, wherein the stopper mechanism comprises a convex portion provided on one of the fixed member and the valve member and a concave portion provided on the other. The differential device according to claim 6 is the differential device according to claim 5, wherein the pin provided on the fixed member is a convex part. The elongated hole of the valve member with which this pin engages is a recess. A differential device according to claim 7 is the differential device according to any one of claims 1 to 4, wherein the stopper mechanism is provided with a convex portion of the fixed-side member and an end of the valve member that abuts against the convex portion to position itself. It is composed of parts and parts.

In any case, the valve member is accurately positioned by these stopper mechanisms, and the same effect as the differential device according to any one of claims 1 to 4 is obtained.

According to the eighth aspect of the present invention, in the differential apparatus, the oil pump is constituted by a plurality of sets of external gear pumps constituted by a sun gear coaxially arranged with the differential case and a plurality of pinion gears arranged on the outer periphery of the sun gear. A valve member, which is arranged so as to sandwich the external gear pump, is formed in a ring shape to integrate the check valve function of each gear pump, and the same effect as the differential device according to any one of claims 1 to 7 is obtained.

In addition to this, four check valves are required for each oil pump, and unlike the conventional example in which a large number of check valves are required for a plurality of sets of oil pumps, a plurality of sets of oil pumps are required. Even if it is used, only two valve members are required, so that the structure is extremely simple, and the number of parts, processing man-hours, and cost are greatly reduced.

[Brief description of drawings]

FIG. 1 is a sectional view showing a first embodiment of the present invention.

FIG. 2 is a plan view of a washer used in the first embodiment.

FIG. 3 is a plan view showing a groove shape and the like of a cover for housing a washer in the first embodiment.

FIG. 4 is a diagram illustrating a check function by rotational movement of a washer in the first embodiment.

FIG. 5 is a diagram illustrating a check function by rotational movement of a washer in the first embodiment.

FIG. 6 is a table showing a washer check function according to a rotation direction of a gear pump in the first embodiment.

FIG. 7 is a plan view of a washer used in the second embodiment of the present invention.

FIG. 8 is a plan view showing a groove shape and the like of a cover for housing a washer in the second embodiment.

FIG. 9 is a plan view of a washer used in a third embodiment of the present invention.

FIG. 10 is a plan view showing a groove shape and the like of a cover for housing a washer in the third embodiment.

FIG. 11 is a plan view of a washer used in a fourth embodiment of the present invention.

FIG. 12 is a plan view showing a groove shape and the like of a cover for housing a washer in the fourth embodiment.

FIG. 13 is a sectional view of a conventional example.

14 is a sectional view taken along line XX of FIG.

[Explanation of symbols]

1 Differential Device 3 Differential Case 7 Cover (Fixed Side Member) 35 Pump Cover (Fixed Side Member) 47 Differential Mechanism 51 Multiple Disc Clutch (Friction Clutch) 53 Hydraulic Actuator 55 Gear Pump (Oil Pump) 73, 119, 137, 155 (ring-shaped first valve member) 75 washer (ring-shaped second valve member) 81, 83 oil port (oil reservoir side) 85 oil port (hydraulic actuator side) 87, oil Pocket (oil reservoir) 95, 157 Round hole (opening part) 97, 123, 125, 141, 143, 159 Closing part 101 Claw (convex part: stopper mechanism) 107 Notch (concave part: stopper mechanism) 121, 139 long hole (Opening part) 129 pins (convex part: stopper mechanism) 131 Long hole (concave part: stopper mechanism) 147 block (Protrusion: stopper mechanism) 151,153,171,173 end (stopper mechanism) 161, 163 valve section 167 projection (stopper mechanism)

Claims (8)

[Claims] 1. A differential case which is rotationally driven by a driving force of an engine, and a differential mechanism which is arranged in the differential case.
The friction clutch that limits the differential of the differential mechanism, the oil pump that is driven by the differential rotation of the differential mechanism and sucks oil from the oil sump, and the friction clutch that receives the oil pressure from the oil pump A hydraulic actuator that presses and fastens, two oil ports on the oil reservoir side that alternately become suction holes and discharge holes as the rotation direction of the oil pump changes, and alternately as the rotation direction of the oil pump changes. Two oil ports on the hydraulic actuator side that serve as suction and discharge holes
When the oil pump reverses to one side and the other side due to the change in the direction of the differential rotation, the oil pump receives the rotation and rotationally moves to the one side and the other side, and the open part becomes the oil reservoir The first valve member that overlaps with the side oil port to open it and closes the oil port on the side of the oil sump where the closed portion becomes the discharge hole, and with the change in the direction of the differential rotation. When the oil pump reverses to one side and the other side, it receives the rotation and rotationally moves to the one side and the other side, and the closed part overlaps with the oil port on the hydraulic actuator side that became the suction hole and closes it. And a second valve member for opening the hydraulic port on the hydraulic actuator side, the opening portion of which serves as a discharge hole, and opening the same, and a stopper mechanism for positioning each valve member at a predetermined position during the movement. Defa, characterized by having Nsharu apparatus. 2. The differential device according to claim 1, wherein the opening portion of the valve member has the same shape as the opening of the oil port and is not smaller than the opening area. 3. The differential device according to claim 1, wherein the opening portion of the valve member is an elongated hole elongated in the moving direction of the valve member. 4. The valve member is a plate-shaped member, and when the valve member moves to one side and the other side, the valve member overlaps with one oil port to form a closed portion that closes the oil port, and overlaps with the other oil port. 2. An opening part that is released to open it.
Differential device. 5. A stopper mechanism includes a convex portion provided on one of the fixed-side member and the valve member, and a concave portion provided on the other of the fixed-side member and the valve member for restricting movement of the convex portion within a predetermined range. The differential device according to any one of claims 1 to 4, comprising: 6. The differential device according to claim 5, wherein the convex portion is a pin provided on the fixed side member, and the concave portion is a long hole provided on the valve member with which the pin engages. 7. The stopper mechanism includes a convex portion of the fixed-side member,
The differential device according to any one of claims 1 to 4, comprising the convex portion and an end portion of a valve member that abuts against the convex portion to position itself. 8. An oil pump is a plurality of sets of external gear pumps having a sun gear arranged coaxially with the differential gear case and a plurality of pinion gears arranged on the outer periphery of the sun gear. Sandwiched between the first and second
Valve members are arranged for the first and second gear pumps.
8. The differential device according to claim 1, wherein one or both of said valve members are integrally formed in a ring shape.