JPS6367431A - Power transmitting device - Google Patents

Abstract

PURPOSE:To enable the distribution of torque between an input shaft and an output shaft to be optionally controlled, by providing a power interrupting clutch, oil pump and an oil pump operating clutch in a power transmitting device suitable for a transfer device in a four wheel driven vehicle. CONSTITUTION:In case of turning off solenoid valve 45 and draining pressure oil in an oil chamber 41 in the engaging direction side of an oil pump operating clutch 40, if an oil pump 31 is driven by an input shaft 11, a movable side oil pump body 30 also rotates in a follow-up motion to the input shaft 11 by driving resistance of the oil pump 31. Consequently, a delivery pressure of the pump 31 is almost zero, and almost no torque is transmitted from the input shaft 11 to an output shaft 13 by almost zeroing also an oil pressure of an oil chamber 51 in the engaging direction side of a power interrupting clutch 50. Accordingly, a perfect condition of two-wheel driving can be obtained in the time of high speed running. While the solenoid valve 45, it it is turned on, increases an oil pressure in the oil chamber 41, and a piston 42 is forced to be firmly attached to the pump body 30, fixing the pump body 30. The clutch 50 is engaged by introducing the delivery pressure of the pump 31 to the oil chamber 51.

Description

[Detailed Description of the Invention] Industrial Application Field The present invention is suitable for use as a power transmission device capable of arbitrarily distributing torque from an input shaft to an output shaft, particularly as a transfer device or a differential limiting device for a four-wheel drive vehicle. This invention relates to a power transmission device.

Prior art and its problems Conventionally, in a four-wheel drive vehicle, a transfer device that automatically transmits torque according to the relative rotational speed between an input shaft and an output shaft is known from Japanese Patent Laid-Open No. 60-252026. . This transfer device includes an oil pump that is driven by a relative rotational speed between a first rotating shaft that drives the front wheels and a second rotating shaft that drives the rear wheels, and an oil pump that is interposed between the first rotating shaft and the second rotating shaft. The oil pump has a clutch equipped therein and an oil passage that guides the discharge pressure of the oil pump to an oil chamber on the engagement direction side of the clutch, and a part of the discharge pressure of the oil pump is drained through an orifice. Therefore, the discharge pressure of the oil pump has a characteristic proportional to the square of the relative rotational speed due to the orifice.

However, in the above case, since the transmitted torque-relative rotational speed characteristic is uniformly determined by the orifice, free torque distribution cannot be performed, and the following problems occur. For example, when driving at high speeds, it is preferable to use full two-wheel drive to improve efficiency;
In the above case, if there is even a slight difference in relative rotational speed due to an imbalance in the shared loads between the front and rear wheels, the oil pump will be driven and the efficiency will drop. Further, even when it is desired to drive the vehicle in four-wheel drive throughout the entire range, in the above case, unless a relative rotational speed difference occurs due to slipping, the four-wheel drive state cannot be achieved, and the driver's intention cannot be met.

OBJECTS OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems, and its object is to provide a power transmission device that can arbitrarily control torque distribution between an input shaft and an output shaft.

Structure of the Invention In order to achieve the above object, the present invention provides a power intermittent clutch provided between an input shaft and an output shaft, an oil pump driven by the input shaft, an operation of the oil pump,
and an oil pump operating clutch that controls non-operation, the hydraulic pressure discharged from the oil pump is guided to an oil chamber on the side in the engagement direction of the power intermittent clutch and the oil pump operating clutch, and the oil pump operating clutch The oil pressure in the oil chamber on the engagement direction side is controlled by an actuator.

DESCRIPTION OF EMBODIMENTS FIGS. 1 and 2 show an example in which the present invention is applied to a transfer device for a FF-based four-wheel drive vehicle.

In FIG. 2, a transmission 2 is mounted on the side of the horizontal engine 1.
The output gear 3 of this transmission 2 meshes with the ring gear 6 of a differential device 5 for driving the front wheels 4. Further, the ring gear 6 meshes with a gear 9 provided at one end of an intermediate shaft 8 via an intermediate gear 7, and a bevel gear 10 provided at the other end of the intermediate shaft 8 is connected to an input shaft 11 of the power transmission device A according to the present invention. It meshes with a bevel gear 12 provided at the tip. A bevel gear 14 provided at the rear end of the output shaft 13 of the power transmission device A is connected to the differential device 1 that drives the rear wheels 15.
It meshes with the ring gear 17 of No. 6.

The power transmission device A has the structure shown in FIG.
And the output shaft 13 is mounted on a bearing 22 by a fixed case 20.21.
, 23, 24. A fixed oil pump body 26 is fixed to the right side of the case 20 by a port 25, and a pump housing 28 is fixed to the left side of the fixed oil pump body 26 with a plate 27 in between with two bolts. .

As shown in FIG. 3, a movable oil pump body 30 is disposed inside the fixed oil pump body 26 and is rotatable coaxially with the input shaft 11. An external gear 32 and an internal gear 33 that constitute the oil pump 31 are arranged. The oil pump 31 is a trochoid type oil pump,
The external gear 32 is a sleeve 34 that rotates integrally with the input shaft 11.
is fitted with a spline. Further, the internal gear 33 is rotatably arranged inside the movable oil pump body 30 so as to be eccentric to the axis of the input shaft 11 . A suction port 35 and a discharge port 36 of an oil pump 31 are formed in the movable oil pump body 30, and the case 20.
The oil collected at the bottom of the oil pump body 21 is sent from a strainer 37 fixed to the lower part of the stationary oil pump body 26 to the suction port 35 through the inside of the stationary oil pump body 26, and is discharged from the discharge port 36. Oil is sent to the gap between the movable oil pump body 30 and the sleeve 34.

The oil discharged from the discharge port 36 flows through the orifice 3
an oil chamber 41 on the engagement direction side of the oil pump operating clutch 40 formed inside the stationary side oil pump body 26 via an oil pump 8; and a power intermittent clutch provided between the input shaft 11 and the output shaft 13. The lubricating oil passage 60 formed in the axial center of the input shaft 11 is supplied via the orifice 39 to the engagement direction side oil chamber 51 of the lubricating oil chamber 50 .

The oil chamber 41 on the engaging direction side of the oil pump operating clutch 40 includes a piston 42 that is movable only in the axial direction with respect to the stationary oil pump body 26, and the piston 42 is attached to the movable oil pump body 30 side. spring 4
3 is accommodated, and the piston 42 is pressed against the side surface of the movable oil pump body 30 by the hydraulic pressure of the oil chamber 41 on the engagement direction side, and the relative rotational speed of the movable oil pump body 30 with respect to the fixed oil pump body 26 is increased. can be controlled.

Further, a drain opening 44 is formed in the lower part of the engagement direction side oil chamber 41, and the oil leaking from this opening 44 is controlled by a solenoid valve 45, which is an example of an actuator. It controls the hydraulic pressure of 41. Solenoid valve 45
is a two-port solenoid valve having an input port and a drain port, and a control signal is inputted to this solenoid valve 45 from a control device (not shown).

In addition to a simple 0N10FF signal, this control signal may also be a duty control signal. In particular, when a duty control signal is input, the oil pressure in the engagement direction side oil chamber 41 is controlled approximately in proportion to the duty ratio. Therefore, it is possible to finely control the engagement force of the oil pump operating clutch 40. Note that the oil discharged from the solenoid valve 45 is collected at the bottoms of the cases 20 and 21.

The power intermittent clutch 50 includes a clutch drum 52 spline-fitted to the rear end of the input shaft 11, a piston 53 disposed inside the clutch drum 52, and a clutch hub integrally formed at the tip of the output shaft 13. 54 and clutch plates 55 and 56 disposed between the clutch drum 52 and the clutch hub 54, the piston 53 is actuated by introducing hydraulic pressure to the engagement direction side oil chamber 51, and the clutch The input shaft 11 and the output shaft 13 can be connected by crimping the plates 55 and 56. The clutch drum 52 is tightened and fixed to the input shaft 11 by a nut 57, and the sleeve 34 is also fixed to the input shaft 11 at the same time by this tightening force.

The oil led to the lubricating oil passage 60 formed in the axial center of the input shaft 11 is supplied to the inside of the clutch plate 55.56 through the needle bearing 61, and lubricates the clutch plate 55.56 by centrifugal force. ing. clutch i55.56
After lubricating the oil, the oil is scattered by centrifugal force, accumulates at the bottom of the case 21, and is sucked into the suction port 35 of the oil pump 31 via the strainer 37 again.

In the power transmission device A having the above structure, the solenoid valve 45 is now turned OFF (fully opened), and the oil pump operating clutch 4
When all the oil pressure in the oil chamber 41 on the engagement direction side 0 is drained, the piston 42 is only in loose pressure contact with the side surface of the movable oil pump body 30 by the spring force of the spring 43, so the oil is drained. When the pump 31 is driven by the input shaft 11, the movable oil pump body 30 also rotates following the human power shaft 11 due to the drive resistance of the oil pump 31. Therefore, the discharge pressure of the oil pump 31 is approximately zero, the oil pressure in the engagement direction side oil chamber 51 of the power intermittent clutch 50 is also approximately zero, and almost no torque is transmitted from the input shaft 11 to the output shaft 13. Therefore, when driving at high speed, a complete two-wheel drive state can be obtained by simply fully opening the solenoid valve 45, and since the discharge pressure of the oil pump 31 is almost zero in the two-wheel drive state. ′
, it is possible to reduce discharge loss and improve efficiency.

On the other hand, when the solenoid valve 45 is turned ON (fully closed), the discharge pressure of the oil pump 31 is directly guided to the oil chamber 41 on the engagement direction side of the oil pump operating clutch 40, so the oil pressure in the oil chamber 41 on the engagement direction side is directly guided. gradually rises, the piston 42 is strongly pressed against the movable oil pump body 30, and the movable oil pump body 30 is fixed. Therefore, oil pump 3
1 increases in accordance with the rotational speed of the input shaft 11, and this discharge pressure is applied to the oil chamber 5 on the engagement direction side of the power intermittent clutch 50.
1, and the clutch 50 is strongly engaged. As a result, the input shaft 11 and the output shaft 13 are directly connected, and four-wheel drive is possible in the entire range.

The solenoid valve 45 is fully open or fully open as described above, as well as 0N10
The operating state of the oil pump 31 can be freely controlled because the opening degree can be adjusted to any desired degree by F F control or duty control. Therefore, the torque distribution from the input shaft 11 to the output shaft 13 can be arbitrarily controlled, and its characteristics can also be arbitrarily controlled. The control factors for the solenoid valve 45 may include the steering angle, the oil temperature, the shared load between the front and rear wheels, the brake signal, the driver's command signal, and the like.

Another Embodiment FIG. 4 shows a second embodiment of the present invention, in which the same parts as in the first embodiment are given the same reference numerals. In this embodiment, an external gear 32, which is a driving member of an oil pump 31, is connected to an input shaft 11 via an oil pump operating clutch 40, and the oil pump body 70 is only a stationary oil pump body. This is different from the first embodiment. As in the first embodiment, one of the discharge pressures of the oil pump 31 is guided through the orifice 38 to the oil chamber 41 on the engagement direction side of the oil pump operating clutch 40 and the solenoid valve 45, and the other is guided to the engagement direction side oil chamber 51 of the power intermittent clutch 50 without going through an orifice, and the other
9 is used for lubrication.

In this case as well, when the solenoid valve 45 is fully open, the oil pump operating clutch 40 is loosely engaged by the force of the spring 43, and as the input shaft 11 rotates, the oil pump
1 is driven and generates a low discharge pressure, but because the solenoid valve 45 is fully open, the oil pump operating clutch 4
It is not guided to the engagement direction side oil chamber 41 of 0. therefore,
The discharge pressure of the oil pump 31 remains low even if the rotational speed of the input shaft 11 increases, and the power intermittent clutch 50 is hardly engaged, resulting in a nearly complete two-wheel drive state.

Furthermore, when the solenoid valve 45 is fully closed, the oil pump 31 is initially driven slightly as the input shaft 11 rotates;
Since the solenoid valve 45 is fully open, the discharge pressure is guided to the oil chamber 41 on the engagement direction side of the oil pump operating clutch 40. As the oil pressure in the oil chamber 41 on the engagement direction side gradually increases to S, the rotation speed of the oil pump 31 increases accordingly, and as a result, the engagement force of the oil pump operating clutch 40 further increases, and the oil pump 31 The rotation speed also increases, and the discharge pressure further increases.Soon, when the oil pump operating clutch 40 becomes fully engaged, the oil pump 31 is moved to the input shaft 11.
The discharge pressure is controlled by the power intermittent clutch 50.
Since the power is directly guided to the oil chamber 51 on the engagement direction side, the power on/off clutch 50 is fully engaged, and the entire range is in a four-wheel drive state.

Note that, of course, by adjusting the opening degree of the solenoid valve 45, the torque distribution from the input shaft 11 to the output shaft 13 can be freely controlled.

In the present invention, the actuator is not limited to an electromagnetic valve, and may be, for example, a manual valve whose opening degree can be adjusted by manual operation, or an electric valve whose opening degree can be adjusted by a stamper motor. Further, the oil pump is not limited to the trochoid type oil pump as in the embodiment, but other oil pumps such as an internal gear type oil pump and a vane pump can also be used.

Effects of the Invention As is clear from the above explanation, according to the present invention, there is a power intermittent clutch provided between the input shaft and the output shaft, an oil pump driven by the input shaft, and the operation of the oil pump. and an oil pump operating clutch that controls non-operation, the hydraulic pressure discharged from the oil pump is guided to an oil chamber on the side in the engagement direction of the power intermittent clutch and the oil pump operating clutch, and the oil pump operating clutch Since the oil pressure in the oil chamber on the engagement direction side is controlled by the actuator, the oil pump discharge oil pressure can be freely controlled by the oil pump operating clutch, and the torque distribution from the input shaft to the output shaft can be freely controlled. can.

Therefore, when the power transmission device of the present invention is applied to a transfer device of a four-wheel drive vehicle, when a complete two-wheel drive state is desired such as when driving at high speed, the actuator disengages the oil pump operating clutch and By putting the pump in a non-operating state, the oil pump does not generate discharge hydraulic pressure, and efficiency can be improved as a complete two-wheel drive state is achieved. In addition, when you want to set the four-wheel drive state, if the actuator fully engages the oil pump operating thalasso and puts the oil pump into operation, all four-wheel drive is possible, regardless of the relative rotational speed between the input shaft and the output shaft. A region four-wheel drive state is also possible.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of a first embodiment of the power transmission device according to the present invention, FIG. 2 is a schematic diagram of an example in which this power transmission device is applied to a four-wheel drive vehicle, and FIG. -m line sectional view, FIG. 4 is a schematic diagram of a second embodiment of the power transmission device. A...Power transmission device, 11...Input shaft, 13...
Output shaft, 26... Fixed side oil pump body, 30.
...Movable oil pump body, 31...Oil pump, 40...Oil pump operating clutch, 41...
・Oil chamber on the engagement direction side, 43... Spring, 45...
Solenoid valve, 50... Clutch for power intermittent, 51... Oil chamber on the engagement direction side. Applicant Daihatsu Motor Co., Ltd. Agent Patent Attorney Hidetaka Tsutsui Figure 2 Figure 3

Claims (4)

[Claims] (1) A power intermittent clutch provided between the input shaft and the output shaft, and an oil pump driven by the input shaft,
an oil pump operating clutch for controlling activation and non-operation of the oil pump; the discharge hydraulic pressure of the oil pump is guided to an oil chamber on the side in the engagement direction of the power intermittent clutch and the oil pump operating clutch; A power transmission device characterized in that a hydraulic pressure in an oil chamber on an engagement direction side of a clutch for operating an oil pump is controlled by an actuator. (2) The oil pump is a trochoid type oil pump, and has a fixed oil pump body and a movable oil pump body inside the fixed oil pump body, and the clutch for operating the oil pump is a trochoid type oil pump. The power transmission device according to claim 1, characterized in that the pump body and the stationary side oil pump body are connected intermittently. (3) The oil pump operating clutch is provided between the drive member of the oil pump and the input shaft, and a spring is disposed in the oil chamber on the engagement direction side of the oil pump operating clutch. A power transmission device according to claim 1. (4) The power transmission device according to any one of claims 1 to 3, wherein the actuator is a solenoid valve.