JPH0735820B2 - Drive connection device for four-wheel drive and hydraulic oil filling method thereof - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention allows transmission of driving force from one side of a front wheel to the other side of a rear wheel by hydraulic pressure generated by a hydraulic pump interposed therebetween. The present invention relates to a four-wheel drive drive connection device that realizes a four-wheel drive state and a method for enclosing hydraulic oil therein.

[Prior art]

Driving by transmitting the driving force of the engine to both the front and rear wheels 4
2. Description of the Related Art Wheel-drive vehicles are in the limelight as being capable of achieving high running stability regardless of road conditions, natural conditions such as weather, and running conditions. In recent four-wheel drive vehicles, a drive connecting device that distributes a driving force according to a rotational speed difference between the front and rear wheels is interposed between the two wheels, and a four-wheel drive state is practically always obtained. A so-called full-time four-wheel drive vehicle configured is mainly used, and as one of the drive coupling devices of this type, there is one that utilizes the hydraulic pressure generated by a hydraulic pump.

This constitutes a hydraulic pump such as a vane pump by coaxially rotatably accommodating a rotor rotating in conjunction with the other in a casing rotating in conjunction with one of the front and rear wheels. The purpose is to generate relative rotation at a speed corresponding to the difference in rotation speed between the rear wheels. With this configuration, inside the hydraulic pump, a hydraulic pressure is generated which becomes higher or lower according to the magnitude of the relative rotation speed, that is, the magnitude of the difference in rotation speed between the front and rear wheels, and between the casing and the rotor. A drive force corresponding to the rotational speed difference between the front and rear wheels is distributed from one of the front and rear wheels to the other through this hydraulic pressure acting to suppress relative rotation between the two, thereby realizing a four-wheel drive state.

By the way, in such a drive coupling device, since the whole is constantly rotated, it is difficult to have a configuration in which the hydraulic oil of the hydraulic pump is supplied from an oil tank fixedly provided on the outside, and it is difficult to provide the hydraulic oil to the outside of the casing. A surrounding member having a thin-walled tubular shape is mounted in a surrounding manner, and an annular chamber formed between the surrounding member and the casing is used as an oil tank. Then, the hydraulic oil in the oil tank is introduced into the hydraulic pump through a suction oil passage formed in a part of the casing, and the oil tank is also introduced through a discharge oil passage also formed in a part of the casing. It is recirculated to and used for circulation.
In order to perform this circulation stably, a suction check valve that allows only the flow from the oil tank to the inside of the hydraulic pump is provided in the suction oil passage, and conversely, in the discharge oil passage, from the inside of the hydraulic pump to the oil tank. Discharge check valves that allow only the flow to the respective are arranged, and further, the discharge oil passage is provided with throttle means for giving a predetermined flow resistance to this circulating flow,
Inside the hydraulic pump, hydraulic pressure is generated against the flow resistance.

[Problems to be Solved by the Invention]

In the drive coupling device having the above-described structure, the working oil is filled in the oil tank and the hydraulic pump at the end of the whole assembly. There is a drawback that it acts as a damper to impede the generation of hydraulic pressure in the hydraulic pump, which adversely affects the transmission characteristics of the driving force. Therefore, conventionally, a method for enclosing the working oil after assembling the working oil by replacing the air with the working oil while sucking the air inside the drive coupling device by vacuum suction has been adopted. The suction check valve mounted and / or the discharge check valve mounted in the discharge oil passage are closed, and there is a drawback that intake is blocked at these mounting positions, and it takes a lot of time for the sealing work, and
There is a possibility that the internal air cannot be completely sucked in and defective transfer characteristics may occur due to the remaining air.

The present invention has been made in view of such circumstances, and a four-wheel drive drive capable of quickly and reliably filling working oil after assembly is completed and preventing characteristic defects due to remaining internal air. An object of the present invention is to provide a connecting device and a method for enclosing hydraulic oil therein.

[Means for Solving the Problems]

The four-wheel drive drive connection device according to the present invention is a casing connected to one of the front wheels or the rear wheels, and a rotor connected to the other of the front wheels or the rear wheels and housed in the casing.
A vane pump type having a plurality of vanes slidably arranged in the rotor in the radial direction and transmitting a driving force by a hydraulic pressure generated in an oil chamber according to a rotational speed difference between the front and rear wheels. A hydraulic pump, and a sealed tank for hydraulic oil integrally formed on the outside of the hydraulic pump, and a suction oil passage having a suction check valve opened in the middle between them by a flow from the latter to the former, In a four-wheel drive drive connection device comprising a discharge check valve which opens by the flow from the former to the latter and a discharge oil passage having an appropriate throttle means in the middle thereof, a discharge check valve and throttle of the discharge oil passage The casing is provided with an intake passage communicating with the means to the outside and an oil injection passage communicating with the inside of the sealed tank or a portion of the suction oil passage on the upstream side of the suction check valve to the outside. age, In the method for filling hydraulic oil according to the present invention applied to a drive connecting device for four-wheel drive, when the hydraulic oil is filled inside the filling tank and the hydraulic pump, the opening end of the intake passage to the outside is a vacuum source. In addition, the open ends of the lubrication passage to the outside are respectively connected to a lubrication source, and while introducing the air inside the sealed tank and the hydraulic pump through the intake passage, the air is introduced through the lubrication hole. It is characterized in that it is replaced with a working oil.

[Action]

In the present invention, the intake air of the internal air of the sealed tank and the hydraulic pump is discharged through the suction check valve and the suction check valve through the suction passage formed in a manner connected to the discharge oil passage between the discharge check valve and the throttle means. Occurs in the direction of opening the check valve,
The flow of hydraulic oil that is replaced by this internal air and introduced into the sealed tank and the hydraulic pump is also directly connected to the inside of the sealed tank, or to the suction oil passage upstream of the suction check valve. It occurs in the direction of opening the suction check valve and the discharge check valve via the oil supply passage formed in a continuous manner.

〔Example〕

Hereinafter, the present invention will be described in detail with reference to the drawings showing an embodiment thereof. FIG. 1 is a vertical cross-sectional view showing an example of a drive connecting device for four-wheel drive according to the present invention (hereinafter referred to as a device of the present invention).

Reference numeral 3 in the drawing denotes a vane pump that acts to connect both wheels by generating hydraulic pressure according to the difference in rotational speed between the front and rear wheels,
It comprises a rotor and a casing that houses the rotor coaxially. The rotor is a cylindrical support cylinder 30c having a diameter smaller than that of both sides of the rotor body 30 having a short cylindrical shape in the axial direction.
It has a shape in which 30c are connected coaxially. As is well known, in the rotor body 30, a plurality of long grooves having a predetermined depth in the radial direction are formed in a substantially equal distribution in the circumferential direction, and each of these vanes 30a having a rectangular flat plate shape, 30a ...
Is slidably inserted in the radial direction. Vane 30a,
The bottoms of the storage grooves of 30a ... Are connected to each other by an annular groove 30b formed on the side surface of the rotor 30, and each vane 30a
Is a radial outside due to the biasing force of a coil spring interposed between this and the bottom of each storage groove and the hydraulic pressure introduced into the bottom of each storage groove via the annular groove 30b as described later. It is designed to be pressed in the direction.

Reference numeral 31 in the drawing has an inner circumference and a circular outer circumference formed by equally arranging three concave portions in the circumferential direction of a circle slightly larger than the outer diameter of the rotor body 30, and is substantially the same as the rotor body 30. It is a cam ring having an uneven wall thickness and having an equal axial length. The casing of the vane pump 3 has side plates 32 and 33 fixed to both sides of the cam ring 31, and is surrounded by the inner peripheral surface of the cam ring 31 and the side surfaces of the side plates 32 and 33 to accommodate the rotor body 30. It is configured to have a cavity portion for inside thereof. One side plate 32 as shown
Has a shape in which a thick-walled cylinder having a diameter smaller than this is coaxially connected to one side of the thick-walled hollow disk, and the other side plate 33 is provided on one side of the thin-walled hollow disk. It has a shape in which thin-walled cylinders having a diameter smaller than this are coaxially connected in series. And these are the cam rings with each cylinder facing outward.
The holding plate 34, the circular plate portion of the side plate 33, and the cam ring 31 are positioned coaxially with the both sides of the holding plate 31 and are loosely fitted to the outside of the cylindrical portion of the side plate 33. Plural fixing bolts that pass through in this order
35, 35 ... (Only one is shown) are screwed into screw holes (not shown) formed in the side plate 32 to be integrated with each other to form the casing. On the outer side of this casing, a thin-walled tubular surrounding member 36 is attached by fitting a part thereof to the outer circumference of the disk portion of the side plate 32 and the outer circumference of the cylindrical portion of the side plate 33, respectively. The operating oil is enclosed in an oil tank T formed in an annular shape between the inner circumference of the surrounding member 36 and the outer circumference of the casing.

In the cylindrical portion of the side plate 32, a bearing bush 32a, a shaft sealing member 32b using an oil seal or the like, and a ball bearing 37.
However, similarly, in the cylindrical portion of the side plate 33, both the bearing bush 32a and the shaft sealing member 32b are internally fitted and fixed in this order from the side of the cam ring 31, and the rotor has bearing cylinders 30c and 30c on both sides. The bearing bushes 32a and 33a are loosely fitted in the bearing bushes 32a and 33a, respectively, and are coaxially and rotatably housed in the casing in such a manner that the end surface of one of the support cylinders 30c abuts the inner ring end surface of the ball bearing 37. At this time, the rotor body 30
The bearing cylinders 30c, 30c, which are located inside the hollow portion 31 inside, are sealed with the shaft sealing members 32b, 33b, which are in close contact with the support cylinders 30c, 30c.

Now, between the outer peripheral surface of the rotor body 30 housed in the cavity inside the cam ring 31 and the inner peripheral surface of the cam ring 31, at the formation position of the recess inside the cam ring 31,
Surrounded by these and the sides of the side plates 32, 33,
A plurality of pump chambers having a modified crescent-shaped axial cross-sectional shape are formed, and these pump chambers are provided with a pair of suction and discharge ports 40, 4 that open to the side plate 32 side at their circumferential ends.
0 (only one is shown). Each suction / discharge port 40 is provided with a separate suction / discharge hole 41 extending in the thickness direction of the side plate 32. The tip of each suction / discharge hole 41 is located radially inward from the outer peripheral surface of the side plate 32. The valve mounting hole 42 is formed to have a predetermined depth in the direction, and is communicated with the middle of each valve mounting hole 42, and the tip of the valve mounting hole 42 has a thickness from the inner surface of the side plate 32. The pressure guide holes 43 extending in the respective directions are communicated with the annular groove 30b on the side surface of the rotor 30. In the valve mounting hole 42, a suction check valve 44 is fitted outside the communication position with the suction discharge hole 41, and a discharge check valve 45 is fitted inside as well. As described above, the oil tank T is formed on the outer side of the side plate 32, the pressure of the hydraulic oil in the oil tank T is provided on one side of the suction check valve 44, and the other side is provided with the pressure of the working oil. The hydraulic pressure in the pump chamber at the opening position of the suction / discharge port 40 acts, and the suction check valve 44 opens when the latter falls below the former, and closes when the latter falls. On the other hand, on one side of the discharge check valve 45, the hydraulic pressure inside the storage groove of the vanes 30a, 30a ... Communicating in the annular chamber 30b is provided, and on the other side, the corresponding opening position of the suction / discharge port 40. The hydraulic pressure inside the pump chamber in FIG. 2 acts, and the discharge check valve 45 opens when the latter exceeds the former, and closes in the opposite case. That is, the suction check valve 44 and the discharge check valve 45 fitted in the same valve mounting hole 42 do not open at the same time, and when the internal pressure of the pump chamber is low, the former is high. The latter opens. Therefore, the enclosed oil in the oil tank T flows radially inward through the valve mounting hole 42 in which the suction check valve 44 is in the open state, and the suction / discharge hole 41 communicating therewith.
Is introduced into the pump chamber through the, and the oil spilled from the pump chamber flows inward in the radial direction in the valve mounting hole 42 in which the discharge check valve 45 is in the open state via the suction discharge hole 41,
It is introduced into the bottom of the storage groove of each vane 30a through the annular groove 30b on the side surface of the rotor body 30. The annular groove 30b is a side plate 32,
The oil flowing into the annular groove 30b communicates with the hollow portion of the shaft 33 and also passes through a slight gap between the one bearing cylinder 30c and the bearing bush 32a into the installation space of the shaft sealing member 32b. It leaks and is returned to the oil tank T through a return hole 46 which has one end opened in the space and which penetrates the disc portion of the side plate 32 in the radial direction.

The device of the present invention configured as described above has an input shaft 1 that rotates in conjunction with one of the front and rear wheels, as indicated by the chain double-dashed line in the figure.
Is internally fitted from the side plate 33 side to the shaft center portion of the rotor to be spline-coupled to the rotor, while the output shaft 2 rotating in conjunction with the other is flange-coupled to the end face of the cylindrical portion of the side plate 32. It is installed between the rear wheels. The tip portion of the input shaft 1 is internally fitted to a ball bearing 37 fitted to the side plate 32, and the set nut 10 screwed onto the outer periphery of the protruding portion from the ball bearing 37 and the end surface of the rotor support cylinder 30c. The inner ring of the ball bearing 37 is clamped and fixed between the two, so that the rotor of the vane pump 3 is
A ball bearing 37 is securely supported inside the casing via the input shaft 1. Thus, since the rotor of the vane pump 3 is interlocked with the input shaft 1 and the casing is interlocked with the output shaft 2 to rotate coaxially separately, a difference in rotational speed occurs between the front and rear wheels. , Relative rotation occurs between the rotor and the casing at a speed corresponding to this difference in rotation speed. The vanes 30a, 30a mounted on the rotor body 30 are urged outward in the radial direction as described above, and when the relative rotation occurs, the tips of the vanes slide on the inner peripheral surface of the cam ring 31. They are brought into contact with each other and move forward and backward along the respective storage grooves and rotate with the rotation of the rotor. The hydraulic oil in each of the pump chambers is sealed between two adjacent vanes 30a, 30a and rotated as the rotor rotates. At the upstream side in the relative rotation direction, the internal pressure of the pump chamber drops. However, the internal pressure rises on the downstream side respectively, and the suction check valve 44 in the valve mounting hole 42 corresponding to the intake / discharge port 40 opening to the upstream side, on the contrary, to the intake / discharge port 40 opening to the downstream side. The discharge check valve 45 is opened in the corresponding valve mounting hole 42. Therefore, the hydraulic oil in the oil tank is sequentially introduced into each pump chamber from the suction / discharge port 40 opening on the upstream side in the relative rotation direction, and the hydraulic oil is rotated in accordance with the rotation of the rotor to increase the pressure, and It is delivered from a suction / discharge port 40 that is open on the downstream side in the rotation direction, and the pressure guide hole 43 and the annular groove 30 are provided.
After being introduced into the bottom of the storage groove of each vane 30a, 30a through b, and pressing the base of each vane 30a outward in the radial direction, a gap between one bearing cylinder 30c and the bearing bush 32a. Then, the oil is recirculated into the oil tank T through the recirculation hole 46. That is, when the suction check valve 44 is open, the valve mounting hole
The outer peripheral half of 42 and the suction / discharge hole 41 function as a suction oil passage, and when the discharge check valve 45 is open, the suction / discharge port 41, the inner half of the valve mounting hole 42, and the pressure guiding hole. 43, annular groove
The gap between the bearing cylinder 30c and the bearing bush 32a and the return hole 46 function as a discharge oil passage.

A part of the hydraulic oil that is sealed and rotated between the vanes 30a, 30a in each pump chamber passes through each of the vanes 30a through an extremely small-diameter throttle hole 30d that passes through the respective vanes 30a, and the low-pressure side (relative rotation direction). It is designed to leak into the same sealed space (upstream side). Inside each pump chamber 40, 40, 40, the throttle hole 30
The hydraulic pressure is generated against the flow resistance in d and the flow resistance in the discharge oil passage, particularly, the flow resistance in flowing through the gap between the support cylinder 30c and the bearing bush 32a. This oil pressure acts between the rotor body 30 and the cam ring 31 to suppress the relative rotation, and the driving force is transmitted from the former to the latter, that is, from the input shaft 1 to the output shaft 2 via this oil pressure. The flow resistance increases as the amount of oil introduced into the pump chamber and the amount of oil delivered from the pump chamber increase, and the amount of these oils varies depending on whether the relative rotational speed between the rotor and the casing is high or low, that is, Since the rotation speed difference between the front and rear wheels is large or small, the hydraulic pressure generated in each pump chamber increases as the rotation speed difference increases. Therefore, the magnitude of the driving force transmitted from the input shaft 1 to the output shaft 2 corresponds to the magnitude of the rotational speed difference between the front and rear wheels, and the magnitude of the rotational speed difference between one of the front and rear wheels changes to the other. Driving force will be distributed and 4
A wheel drive condition is realized.

That is, in the drive coupling device of this type, the oil contained in the oil tank T is circulated and used in each pump chamber, and the driving force is transmitted by the hydraulic pressure generated in each pump chamber. In the case where air is mixed in the hydraulic oil previously filled in T and each pump chamber, this air acts as a damper to hinder the generation of hydraulic pressure, and as a result, a proper driving force transmission characteristic cannot be obtained. Therefore, it is important to ensure that the hydraulic oil is sealed.

FIG. 2 is a vertical cross-sectional view of the device of the present invention taken along a cross section different from that of FIG. 1, and shows a working state of the method for enclosing hydraulic oil according to the present invention (hereinafter referred to as the method of the present invention).

As shown in this figure, the device of the present invention is provided with an intake hole 5 and an oiling hole 6 which are opened at one end of the side plate 32 and which extend in the axial direction, respectively, on the end face of the side plate 32. Can be implemented.

The intake hole 5 is formed in one side of the rotor 30 by a communication hole 50 formed by opening one end on the inner surface of the side plate 32 and inclining radially outward from the open end. It communicates with the groove 30b. This annular groove 30b
Is a part of the discharge oil passage of the vane pump 3 and is located between the discharge check valve 45 and the gap between the bearing cylinder 32c and the bearing bush 32a which functions as a throttle means as described above. . That is, the intake check hole and the communication hole 50 allow the discharge check valve in the discharge oil passage of the vane pump 3.
An intake passage is formed that communicates between the 45 and the throttle means to the outside.

On the other hand, the oiling hole 6 has one end opened to the outer peripheral surface of the side plate 32, and a communication hole 60 extending inward in the radial direction from the opening end communicates with the oil tank T formed outside the side plate 32. Has been done. That is, the oil injection hole 6 and the communication hole 60 constitute an oil injection passage that connects the inside of the oil tank T to the outside. The communication hole 60 may be opened not only on the outer periphery of the side plate 32 but also on the upstream side of the mounting position of the suction check valve 43 in the suction oil passage of the vane pump 3 described above. The oil passage structure shown in FIG. 2 is formed, and the formation of the communication passage 60 that connects the oil injection hole 6 shown in FIG. 2 and the suction oil passage formed as described above is realistic as is clear from the comparison between both drawings. is not.

In addition, such an intake hole 5, a communication hole 50, and an oil filling hole 6
The communication hole 60 and the communication hole 60 may be provided in one set, but a plurality of sets may be provided in the circumferential direction as long as the arrangement position can be secured.

When the method of the present invention is carried out in the apparatus of the present invention configured as described above, first, after the assembly is completed, first, the intake hole 5
While one end of the intake pipe 7 is screwed and fixed to the female screw portion 51 formed at the opening end to the outside, as shown by the two-dot chain line in the figure,
Similarly, one end of the oiling pipe 8 is screwed and fixed to a female screw portion 61 formed at the opening end of the oiling hole 6 to the outside, and the other end of the intake pipe 7 is connected to a vacuum source (not shown) and the oiling pipe 8 The other end of each of these is connected to an oiling tank (not shown). Next, the vacuum source is operated, and the air in the internal space of the vane pump 3 and the oil tank T formed outside the vane pump 3 is blanked in the drawing through the intake pipe 7, the intake hole 5, and the communication hole 50. Inhale as indicated by the arrow. As a result, the oil in the lubrication tank is
The oil is injected into the inside of the oil tank T and the internal space of the vane pump 3 through the oil injection pipe 8, the oil injection hole 6 and the communication hole 60 so as to be replaced by the intake air and is filled therein.

Now, the intake hole 5 is connected to the annular groove 30b through the communication hole 50.
Since the air in the oil tank T flows radially inward in the valve mounting hole 42, the pressure guiding hole 43
The air in each pump chamber reaches the inside of the valve mounting hole 42 through the suction / discharge port 40 and the suction / discharge hole 41, respectively. ,
The gas flows inward in the hole 42 in the radial direction, and further, is similarly sucked into the communication hole 50 and the suction hole 5 through the pressure guiding hole 43 and the annular groove 30b. That is, when air is taken in through the intake hole 5, the air in the oil tank T and each pump chamber has a valve mounting hole 42 in which the suction check valve 44 and the discharge check valve 45 are mounted.
The flow is inward in the radial direction, and this flow direction is the direction in which the suction check valve 44 and the discharge check valve 45 are opened as described above.
It will be done promptly without being disturbed.

Further, since the oil filling hole 6 is communicated with the inside of the oil tank T through the communication hole 60, the working oil supplied through the oil filling hole 6 directly flows into the oil tank T, and , Each pump chamber has a valve mounting hole from the open end of the outer periphery of the side plate 32.
After flowing radially inward in 42, separate suction and discharge holes 41
And, it flows in through the suction / discharge port 40, and then the vanes 30a, 30a ...
After flowing inward in the vane mounting hole 42 to the bottom of the storage groove, it flows in through the pressure guiding hole 43. That is, the hydraulic oil introduced through the oil injection hole 6 is directly introduced into the oil tank T, and the valve mounting hole 42 is provided in the internal space of the vane pump 3.
Is introduced by flowing inward in the radial direction, and this flow direction is the direction in which the suction check valve 44 and the discharge check valve 45 are opened.
It is surely done without being disturbed.

As described above, according to the method of the present invention, the suction check valve 44 and the discharge check valve 45 are used for the intake space in the internal space of the vane pump 3 and the oil tank T formed outside the vane pump 3, and the lubrication to these spaces. Is performed in the direction of opening the, and the filling of hydraulic oil into these spaces can be done quickly and reliably,
There is no risk of air remaining after the hydraulic oil is filled.

FIG. 3 is a vertical cross-sectional view of a drive coupling device for four-wheel drive having a structure different from that shown in FIGS. 1 and 2. The drive coupling device shown in the figure is the above-mentioned bearing cylinder forming a part of the rotor.
Rather than supporting the outer peripheries of 30c, 30c, the rotor shaft 9 inserted from the outside into the casing is fitted in the axial center position of the rotor body 30 and spline-coupled with this.
The bearings are fitted to the side plates 32, 33 by means of respective bearings, and the inside and outside of the vane pump 3 are also sealed not at the outer circumference of the supporting cylinders 30c, 30c but at one side. Is a shaft sealing member fitted in the side plate 33.
A cover plate that is internally fitted and fixed to the hollow portion of the side plate 32 between the outer peripheral surface of the rotor shaft 9 and 33c.
It is configured to be performed by 32c. Further, the suction and discharge ports of the pump chambers are not centrally provided on the side plate 32 on one side unlike the drive coupling device shown in FIG. 1, and only the discharge dedicated port is provided on the side plate 32 side. Side plate 33
There is a suction port on the side. Each of the discharge-only ports is made to communicate with the annular groove 30c on the side surface of the rotor body 30 by the folding hole 47 formed in the side plate 32.
A discharge check valve 45 is attached midway through 7. Thus, the discharge oil passage of the vane pump 3 includes the return hole 47, the bottom of the storage groove, both side surfaces of the rotor body 30, and the side plates 32, 33.
And the side plates 32, 33 and the return hole 46. Further, a suction-dedicated port is provided on the side plate 33 side, these are formed in such a manner as to penetrate the side plate 33 and the pressing plate 34 in the thickness direction, and the suction check valve 44 is fitted midway. The oil tank T is communicated with the suction hole 48. Thus, the suction oil passage of the vane pump 3 is constituted only by this suction hole 48. Other configurations and operations are substantially the same as those shown in FIG.
The same reference numerals as those in the figure are given and the description thereof is omitted.

Also in the drive coupling device having such a configuration, as shown by a broken line in the drawing, one end is opened to the outer surface of the side plate 32, and the intake hole 5 and the oil filling hole 6 extending in the thickness direction thereof are formed. And the former is communicated with the annular groove 30b through the communication hole 50 and the latter is communicated with the oil tank T through the communication hole 60, it is possible to carry out the method of the present invention described above. The hydraulic oil can be quickly and reliably filled in the tank T and the vane pump 3. In addition,
At this time, the inside of the annular groove 30b, which is the opening position of the communication hole 50, is located between the discharge check valve 45 in the discharge oil passage and the gap on both sides of the rotor body 30 functioning as throttle means. Would be obvious.

〔effect〕

As described in detail above, in the device of the present invention, since torque is transmitted between the front and rear wheels via the hydraulic pressure generated in the oil chamber between the casing and the rotor, wear and vibration of device components are generated. Low, long life, high reliability and good usability.

Further, since the intake passage communicates with the outside between the discharge check valve in the discharge oil passage and the throttling means, the discharge oil is discharged to the low pressure portion through the throttling means, so that the increase in hydraulic pressure increases the rotation speed. It becomes gradual with the increase of the difference, and it is not necessary to provide an intake passage on the upstream side of the intake check valve of the sealed tank and the intake oil passage, that is, in the low pressure part, and the number of intake passages can be reduced, and the structure of the casing and rotor Simplification, easy manufacture, and cost reduction.

Furthermore, by connecting a vacuum source to the opening to the outside of the intake passage when filling the hydraulic oil, it is possible to create a vacuum inside the equipment such as the enclosed tank, pump chamber, and lubrication passage that are connected to the intake passage. When the oil is filled, both the flow of the intake air and the oil supply occur only in the direction of opening the suction check valve and the discharge check valve, so that both the check valves do not hinder the intake and the oil supply. The present invention is such that the hydraulic oil can be quickly and surely filled in the pump, the filling work can be speeded up, and air remains inside the hydraulic pump, resulting in no characteristic failure due to the remaining air. Has an excellent effect.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view showing an example of the device of the present invention, FIG. 2 is a view showing an implementation state of the method of the present invention in the device of the present invention shown in FIG. 1, and FIG. 3 is another embodiment of the device of the present invention. FIG. 3 ... Vane pump, 5 ... Intake hole, 6 ... Lubrication hole, 7 ... Intake pipe, 8 ... Lubrication pipe, 30 ... Rotor body, 31 ... Cam ring, 3
2, 33 ... Side plate, 36 ... Enclosure member, 40 ... Suction discharge port, 41 ... Suction discharge hole, 43 ... Pressure guide hole, 44 ... Suction check valve, 45 ... Discharge check valve, T ... Oil tank

Claims (2)

[Claims] 1. A casing connected to one of a front wheel and a rear wheel, a rotor connected to the other of the front wheel and a rear wheel and housed in the casing, and a rotor slidably disposed in the rotor. A vane pump type hydraulic pump having a plurality of vanes formed therein and transmitting the driving force by the hydraulic pressure generated in the oil chamber according to the rotational speed difference between the front and rear wheels, and integrally on the outside thereof. A suction oil passage having a formed hydraulic oil filling tank and having a suction check valve in the middle between which the latter is opened by the flow from the latter to the former, and a discharge check valve which is opened by the flow from the former to the latter. And a drive connecting device for four-wheel drive, which comprises a discharge oil passage having an appropriate throttle means in the middle thereof, and an intake passage communicating between the discharge check valve of the discharge oil passage and the throttle means to the outside. , The enclosed tongue A drive connection device for four-wheel drive, wherein the casing is provided with an oil injection passage that communicates the inside of the cylinder or the upstream side of the suction check valve of the suction oil passage with the outside. 2. When the working oil is filled in the sealed tank and the hydraulic pump, the opening end of the intake passage to the outside is used as a vacuum source, and the opening end of the lubrication passage to the outside is used as an oil supply source, respectively. The connection is made, and while the internal air of the sealed tank and the hydraulic pump is sucked in through the intake passage, the air is replaced with hydraulic oil introduced through the oil filling hole. A method for enclosing hydraulic oil in a drive coupling device for four-wheel drive.