JP4962189B2 - Hydraulic clutch control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a controller of hydraulic clutches capable of realizing accurate clutch engagement control by suppressing the dispersion of working pressure between the clutches. <P>SOLUTION: This controller of hydraulic clutches comprises an oil pump 13, a pressure regulating valve 14, a selector valve 15 capable of changing over between a first state in which the communication between a first oil path 21 and a third oil path 23 and the communication between a second oil path 22 and a fourth oil path 24 and a second state in which the communication between the first oil path 21 and the fourth oil path 24 and the communication between the second oil path 22 and the third oil path 23, and a control means for controlling the tightening forces of the first hydraulic clutch 9 and the second hydraulic clutch 10 by changing the discharge pressure of the oil pump 13, the output pressure of the pressure regulating valve 14, and the state of the selector valve 15. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

  The present invention belongs to the technical field of hydraulic clutch control devices.

As a mechanism for controlling the fastening force of two hydraulic clutches with one oil pump, a mechanism in which each hydraulic clutch is provided with a pressure regulating valve for controlling the fastening force is known (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 2-109738

  However, in the above-described prior art, since two pressure regulating valves are used, there is a problem that there is a large operating pressure variation between the clutches because there is a variation in each pressure regulating valve in the operating pressure of each clutch. It was.

  The present invention has been made to solve the above problems, and an object of the present invention is to provide a hydraulic clutch control device that can suppress variation in operating pressure between clutches and realize high-precision clutch engagement control. There is to do.

In order to achieve the above object, the present invention provides:
An oil pump,
A pressure regulating valve for regulating the input hydraulic pressure to a desired pressure;
A pump discharge oil passage communicating the discharge port of the oil pump and the input port of the pressure regulating valve;
A first oil passage communicating with the output port of the pressure regulating valve;
A second oil passage communicating with the pump discharge oil passage;
A third oil passage communicating with the hydraulic chamber of the first hydraulic clutch;
A fourth oil passage communicating with the hydraulic chamber of the second hydraulic clutch;
A first state for maintaining communication between the first oil passage and the third oil passage and communication between the second oil passage and the fourth oil passage; and the first oil passage and the fourth oil passage. A switching valve capable of switching between a second state that maintains communication with the second oil passage and the communication between the second oil passage and the third oil passage;
Control means for changing the discharge pressure of the oil pump, the output pressure of the pressure regulating valve and the state of the switching valve, and controlling the fastening force of the first hydraulic clutch and the second hydraulic clutch;
It is characterized by providing.

In the hydraulic clutch control device of the present invention, the engagement force between the first hydraulic clutch and the second hydraulic clutch is arbitrarily controlled by changing the discharge pressure of the oil pump, the output pressure of the pressure regulating valve, and the state of the switching valve. be able to. At this time, in the present invention, since the two clutch operating pressures can be determined by one pressure regulating valve, the operating pressure variation between the clutches can be suppressed within the range of the variation of one pressure regulating valve.
As a result, the operating pressure variation between the clutches can be kept small, and highly accurate clutch engagement control can be realized.

  Hereinafter, the best mode for carrying out the present invention will be described based on Examples 1 to 3.

First, the configuration will be described.
FIG. 1 is an overall configuration diagram showing a drive system of a rear wheel drive vehicle to which a hydraulic clutch control device of Embodiment 1 is applied.

  In the rear wheel drive vehicle of the first embodiment, the output of the engine 1 decelerated by the automatic transmission 2 is transmitted to the differential gear 4 via the propeller shaft 3, and the left and right drive axles 5 and 6 are transmitted from the differential gear 4 to the left and right drive axles 5 and 6. It is transmitted to the rear wheels 7 and 8. The left and right drive axles 5, 6 are provided with torque transmission clutches (first hydraulic clutch, second hydraulic clutch) 9, 10, respectively.

  The torque transmission clutches 9 and 10 are hydraulic clutches, and their fastening force is controlled by the controller 12 via the control valve unit 11. The controller 12 outputs a command for controlling the fastening force of the torque transmission clutches 9 and 10 to the control valve unit 11 based on the required driving force difference set according to the traveling state.

  For example, when one of the left and right rear wheels 7 and 8 idles during straight running, the fastening force of the torque transmission clutch on the idle wheel side is reduced, and the engine output is largely distributed to the other wheel. Thereby, idling of a wheel is suppressed and a driving force fall can be controlled. Further, during turning, the fastening force of one torque transmission clutch is increased according to the turning direction, and the fastening force of the other torque transmission clutch is reduced, and a left / right rear wheel 7, 8 generates a left / right driving force difference. Thereby, a yaw moment is given to a vehicle and turning performance can be improved.

FIG. 2 is a diagram illustrating the configuration of the control valve unit 11 according to the first embodiment. The control valve unit 11 includes an oil pump 13, a pressure regulating valve 14, and a switching valve 15.
For example, a gear pump is used as the oil pump 13 and is driven by an electric motor 13b.

  The pressure regulating valve 14 is a pressure reducing valve that reduces the hydraulic pressure input to the input port 14a to a desired pressure and discharges it from the output port 14b. The input port 14 a communicates with the discharge port 13 a of the oil pump 13 through a pump discharge oil passage 16.

The switching valve 15 is a spool type switching valve provided with a valve housing 17, a spool 18, a solenoid 19, and a spring 20.
The valve housing 17 is formed with a first input port 17a, a second input port 17b, a first output port 17c, a second output port 17d, and a third output port 17e.

The first input port 17 a is connected to the output port 14 b of the pressure regulating valve 14 through the first oil passage 21. The second input port 17 b is connected to the pump discharge oil passage 16 and the second oil passage 22.
The first output port 17 c is connected to the hydraulic chamber 9 a of the first hydraulic clutch 9 through the third oil passage 23. The second output port 17 d is connected to the hydraulic chamber 10 a of the second hydraulic clutch 10 by the fourth oil passage 24. The third output port 17 e is connected by the third oil passage 23 and the oil passage 25.

  The spool 18 is a first spool position that maintains communication between the first input port 17a and the first output port 17c, communication between the second input port 17b and the second output port 17d, and closing of the third output port 17e. (See FIG. 5), the second input port 17a and the second output port 17d are connected to each other, the second input port 17b and the third output port 17e are connected to each other, and the first output port 17a is closed. Between the two spool positions (see FIG. 2).

  The spool 18 is in the second spool position (second state) by the urging force of the spring 20 when the solenoid 19 is in a non-energized state, and resists the urging force of the spring 20 when the solenoid 19 is in an energized state. Move to the first spool position (first state).

  The controller (control means) 12 is a required driving force that sets the discharge pressure of the oil pump 13 (output torque of the electric motor 13b), the output pressure of the pressure regulating valve 14, and the state of the switching valve 15 according to the running state. Control based on the difference.

Next, the operation of the control valve unit 11 will be described.
(If the fastening force is the same)
When the fastening forces of the first hydraulic clutch 9 and the second hydraulic clutch 10 are the same, the pressure regulating valve 14 is opened, that is, without adjusting the pressure reduction, the oil pump 13 is driven and the discharge pressure is set to the first hydraulic pressure. The desired pressure required for the clutch 9 and the second hydraulic clutch 10 is set. At this time, the switching valve 15 may be in either the first state or the second state.

  For example, when the switching valve 15 is in the second state, as shown in FIG. 3, the discharge pressure of the oil pump 13 is such that the pump discharge oil passage 16 → the pressure regulating valve 14 → the first oil passage 21 → the first input port 17a. → Second output port 17d → Supply to the second hydraulic clutch 10 via the fourth oil path 24, and at the same time, the pump discharge oil path 16 → second oil path 22 → second input port 17b → third output It is supplied to the first hydraulic clutch 9 via the port 17e → oil path 25. Thereby, since the discharge pressure of the oil pump 13 is supplied to both the first hydraulic clutch 9 and the second hydraulic clutch 10 as the operating pressure, the two clutches 9 and 10 can have the same fastening force.

(When different fastening force is used)
When changing the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10, for example, when making the fastening force of the first hydraulic clutch 9 high and lowering the fastening force of the second hydraulic clutch 10, the switching valve 15 is turned on. 2, the oil pump 13 is driven and its discharge pressure is adjusted to a desired pressure required by the first hydraulic clutch 9, and the pressure regulating valve 14 is driven and its output pressure is adjusted by the second hydraulic clutch 10. Depressurize to the desired pressure required.

  As a result, as shown in FIG. 4, the discharge pressure of the oil pump 13 is supplied to the first hydraulic clutch 9 as the operating pressure, and the output pressure of the pressure regulating valve 14 is supplied to the second hydraulic clutch 10 as the operating pressure. Therefore, the fastening force of the first hydraulic clutch 9 can be increased and the fastening force of the second hydraulic clutch 10 can be reduced.

(When switching fastening force)
When switching the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 from the state of FIG. 4, the switching valve 15 is switched from the second state to the first state. At this time, as shown in FIG. 5, the discharge pressure of the oil pump 13 input to the second input port 17b is supplied to the second hydraulic clutch 10 via the second output port 17d → the fourth oil passage 24. Then, the output pressure of the pressure regulating valve 14 input to the first input port 17 a is supplied to the first hydraulic clutch 9 via the first output port 17 c → the third oil passage 23.

  As a result, from the state where the fastening force of the first hydraulic clutch 9 is high and the fastening force of the second hydraulic clutch 10 is low, the fastening force of the first hydraulic clutch 9 is low and the fastening force of the second hydraulic clutch 10 is high. And can be switched instantly.

[Reduction in operating pressure variation]
In the first embodiment, one oil pump 13, one pressure regulating valve 14, and one switching valve 15 are used, and the controller 12 controls the discharge pressure of the oil pump 13, the output pressure of the pressure regulating valve 14, and the state of the switching valve 15. Thus, the fastening force of the two hydraulic clutches 9 and 10 can be freely controlled.

  That is, the two hydraulic clutches 9 and 10 can have the same fastening force by disabling the pressure regulating valve 14 and adjusting the discharge pressure of the oil pump 13. Further, by operating both the oil pump 13 and the pressure regulating valve 14, the discharge pressure of the oil pump 13 is supplied to one of the two hydraulic clutches 9 and 10 according to the state of the switching valve 15, and the pressure regulating valve 14 to the other. Therefore, the fastening force of one clutch can be increased and the fastening force of the other clutch can be reduced. Furthermore, by switching the state of the switching valve 15 from a state in which the fastening force of one clutch is high and the fastening force of the other clutch is low, the fastening force of one clutch is instantaneously reduced and the fastening force of the other clutch is reduced. Can be high.

  Conventionally, when controlling the operating pressure of two clutches, a total of two pressure regulating valves have been used, one for each clutch. However, since there are variations in the pressure regulating valves, the operating variation between the clutches becomes large. There was a problem.

  On the other hand, in the control valve unit 11 of the first embodiment, only one pressure regulating valve 14 is used, and the switching valve 15 is stable in input / output, so there is no fear of variation. The operating pressure variation can be suppressed within the range of variation of one pressure regulating valve 14. Moreover, since the switching valve 15 is very cheap compared with a pressure regulation valve, it can be set as a low-cost system.

Next, the effect will be described.
In the hydraulic clutch control apparatus according to the first embodiment, the following effects can be obtained.

  (1) an oil pump 13, a pressure regulating valve 14 that regulates the input hydraulic pressure to a desired pressure, a pump discharge oil passage 16 that communicates the discharge port 13a of the oil pump 13 and the input port 14a of the pressure regulating valve 14, A first oil passage 21 communicating with the output port 14b of the pressure regulating valve 14, a second oil passage 22 communicating with the pump discharge oil passage 16, and a third oil passage 23 communicating with the hydraulic chamber 9a of the first hydraulic clutch 9. A fourth oil passage 24 communicating with the hydraulic chamber 10a of the second hydraulic clutch 10, a communication between the first oil passage 21 and the third oil passage 23, and a communication between the second oil passage 22 and the fourth oil passage 24. Switching between the first state for maintaining the first oil passage 21 and the fourth oil passage 24 and the second state for maintaining the second oil passage 22 and the third oil passage 23. Possible switching valve 15, discharge pressure of oil pump 13, output pressure of pressure regulating valve 14 and switching A controller 12 that changes the state of the valve 15 and controls the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10. Thereby, the operating pressure variation between clutches can be suppressed small, and highly accurate clutch engagement force control can be realized.

  (2) Since the changeover valve 15 is a spool type changeover valve, highly responsive clutch engagement control can be realized.

  (3) The spool type switching valve is connected to the first input port 17 a connected to the first oil passage 21, the second input port 17 b connected to the second oil passage 22, and the third oil passage 23. The first output port 17c, the second output port 17d connected to the fourth oil passage 24, the third output port 17e connected to the third oil passage 23, the first input port 17a and the first output port 17c A first spool position corresponding to a first state for maintaining communication with the second input port 17b and the second output port 17d and closing the third output port 17e, and the first input port 17a. A second spool position corresponding to a second state that maintains communication with the second output port 17d, communication between the second input port 17b and the third output port 17e, and closing of the first output port 17c; A spool 18 for switching Yeah. Thereby, highly responsive clutch engagement control can be realized.

  (4) The first hydraulic clutch 9 and the second hydraulic clutch 10 are torque transmission clutches that transmit power from the power source (engine 1) to the left and right rear wheels 7 and 8, and the controller 12 is set according to the traveling state. Based on the required driving force difference, the discharge pressure of the oil pump 13, the output pressure of the pressure regulating valve 14, and the state of the switching valve 15 are changed. Thereby, the operating pressure variation between clutches can be suppressed small, and highly accurate left and right driving force distribution control can be realized.

Example 2 is an example in which a rotary switching valve is used as the switching valve.
The overall configuration of the vehicle is the same as that of the first embodiment shown in FIG.

  FIG. 6 is a diagram illustrating a configuration of the control valve unit 30 according to the second embodiment. In the second embodiment, an oil passage 22 ′ connected to the second oil passage 22 is provided.

  The switching valve 31 of the second embodiment is a rotary switching valve that switches paths by rotation, and the valve body 32 is formed in a columnar shape, and a plurality of paths 32a to 32e are formed therein as shown in FIG. Is set.

The path 32b is disposed on a straight line passing through the center of the valve body 32, and paths 32a and 32c are disposed on both sides thereof. The path 32d is formed in a substantially U shape, and is disposed at a position on the path 32a side of the valve body 32. The path 32e is formed in a substantially U-shape and is disposed at a position on the path 32c side of the valve body 32.
The valve body 32 is operated by controlling the angle of the stepping motor 33 (see FIG. 8), and the communication between the first oil passage 21 and the third oil passage 23 and the communication between the second oil passage 22 and the fourth oil passage 24 are performed. The second state of maintaining the first state (see FIG. 10), the communication between the first oil passage 21 and the fourth oil passage 24, and the communication between the second oil passage 22 and the third oil passage 23. Maintaining communication between the state (see FIG. 6), the third state (see FIG. 11) in which the third oil passage 23 and the fourth oil passage 24 are blocked, and the third oil passage 23 and the fourth oil passage 24, respectively. The fourth state (see FIG. 12) is switched.

Next, the operation of the control valve unit 30 will be described.
(If the fastening force is the same)
When the fastening forces of the first hydraulic clutch 9 and the second hydraulic clutch 10 are the same, the pressure regulating valve 14 is opened, that is, without adjusting the pressure reduction, the oil pump 13 is driven and the discharge pressure is set to the first hydraulic pressure. The desired pressure required for the clutch 9 and the second hydraulic clutch 10 is set. At this time, the switching valve 31 may be in either the first state or the second state.

  For example, when the switching valve 31 is in the second state, as shown in FIG. 6, the discharge pressure of the oil pump 13 is such that the pump discharge oil path 16 → the pressure regulating valve 14 → the first oil path 21 → the path 32 b → the fourth. At the same time as being supplied to the second hydraulic clutch 10 via the oil path 24, the pump discharge oil path 16 → the second oil path 22 → the path 32 a → the third oil path 23 to the first hydraulic clutch 9. Supplied with. Thereby, since the discharge pressure of the oil pump 13 is supplied to both the first hydraulic clutch 9 and the second hydraulic clutch 10 as the operating pressure, the two clutches 9 and 10 can have the same fastening force.

(When different fastening force is used)
When changing the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10, for example, when increasing the fastening force of the first hydraulic clutch 9 and lowering the fastening force of the second hydraulic clutch 10, the switching valve 31 is set to 2, the oil pump 13 is driven and its discharge pressure is adjusted to a desired pressure required by the first hydraulic clutch 9, and the pressure regulating valve 14 is driven and its output pressure is adjusted by the second hydraulic clutch 10. Depressurize to the desired pressure required.

  As a result, as shown in FIG. 9, the discharge pressure of the oil pump 13 is supplied to the first hydraulic clutch 9 as the operating pressure, and the output pressure of the pressure regulating valve 14 is supplied to the second hydraulic clutch 10 as the operating pressure. Therefore, the fastening force of the first hydraulic clutch 9 can be increased and the fastening force of the second hydraulic clutch 10 can be reduced.

(When switching fastening force)
When switching the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 from the state of FIG. 9, the switching valve 31 is switched from the second state to the first state. At this time, as shown in FIG. 10, the oil passage 22 ′ connected to the second oil passage 22 and the fourth oil passage 24 communicate with each other, and the first oil passage 21 and the oil passage 25 communicate with each other. The discharge pressure of the pump 13 is supplied to the second hydraulic clutch 10 via the fourth oil passage 24, and the output pressure of the pressure regulating valve 14 is supplied from the oil passage 25 via the third oil passage 23 to the first hydraulic pressure. It is supplied to the clutch 9.

  As a result, from the state where the fastening force of the first hydraulic clutch 9 is high and the fastening force of the second hydraulic clutch 10 is low, the fastening force of the first hydraulic clutch 9 is low and the fastening force of the second hydraulic clutch 10 is high. And can be switched instantly.

(Fastening force retention)
When the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 is maintained, the switching valve 31 is switched to the third state, that is, the state in which the third oil passage 23 and the fourth oil passage 24 are shut off (see FIG. 11). Thereby, since the hydraulic pressure supplied to both hydraulic chambers 9a and 10a is maintained, the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 can be maintained.

(Average fastening force)
When the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 is averaged from the state in which the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 is different, the switching valve 31 is set to the fourth state. That is, the third oil passage 23 and the fourth oil passage 24 are switched to a state where they are communicated with each other via the passage 32e (FIG. 12). Thereby, since the hydraulic pressure supplied to both hydraulic chambers 9a and 10a is averaged, the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 can be instantaneously made equal.

Next, the effect will be described.
In the hydraulic clutch control device of the second embodiment, in addition to the effects (1) and (4) of the first embodiment, the following effects can be obtained.

  (5) Since the switching valve 31 can be switched to the third state in which the third oil passage 23 and the fourth oil passage 24 are shut off, the first hydraulic clutch 9 and the second hydraulic clutch 9 can be switched only by the operation of the switching valve 31. The fastening force of the hydraulic clutch 10 can be held instantaneously.

  (6) Since the switching valve 31 can be switched to the fourth state in which the communication between the third oil passage 23 and the fourth oil passage 24 is maintained, only the operation of the switching valve 31 causes the first hydraulic clutch 9 and The fastening force of the second hydraulic clutch 10 can be instantly averaged.

  (7) Since the switching valve 31 is a rotary switching valve, a switching valve that switches between the first state, the second state, the third state, and the fourth state can be realized with a simple configuration.

The third embodiment is an example in which a rotary switching valve is used with respect to the second embodiment.
The overall configuration of the vehicle is the same as that of the first embodiment shown in FIG.

  FIG. 13 is a diagram illustrating the configuration of the control valve unit 40 according to the third embodiment. The switching valve 41 is formed in a columnar shape, and a plurality of paths 42a to 42d are formed therein as shown in FIG. Is set. The paths 42a and 42b are arranged on the straight lines that pass through the center of the valve main body 42 and are orthogonal to each other. The paths 42c and 42d are formed in a substantially U-shape, and have the same height as the path 42b. Has been placed.

  The valve body 42 operates by controlling the angle of the stepping motor, as in the second embodiment, and the communication between the first oil passage 21 and the third oil passage 23 and the communication between the second oil passage 22 and the fourth oil passage 24. The second state of maintaining the first state (see FIG. 15), the communication between the first oil passage 21 and the fourth oil passage 24, and the communication between the second oil passage 22 and the third oil passage 23. A state (see FIG. 13), a third state in which the third oil passage 23 and the fourth oil passage 24 are respectively blocked, and a fourth state in which communication between the third oil passage 23 and the fourth oil passage 24 is maintained. And switch.

Next, the operation of the control valve unit 40 will be described.
(If the fastening force is the same)
When the fastening forces of the first hydraulic clutch 9 and the second hydraulic clutch 10 are the same, the pressure regulating valve 14 is opened, that is, without adjusting the pressure reduction, the oil pump 13 is driven and the discharge pressure is set to the first hydraulic pressure. The desired pressure required for the clutch 9 and the second hydraulic clutch 10 is set. At this time, the switching valve 41 may be in either the first state or the second state.

  For example, when the switching valve 41 is in the second state, as shown in FIG. 13, the discharge pressure of the oil pump 13 is such that the pump discharge oil passage 16 → the pressure regulating valve 14 → the first oil passage 21 → the passage 42d → the fourth. At the same time, the oil is supplied to the second hydraulic clutch 10 via the oil passage 24 and at the same time to the first hydraulic clutch 9 via the pump discharge oil passage 16 → the second oil passage 22 → the passage 42 c → the third oil passage 23. Supplied with. Thereby, since the discharge pressure of the oil pump 13 is supplied to both the first hydraulic clutch 9 and the second hydraulic clutch 10 as the operating pressure, the two clutches 9 and 10 can have the same fastening force.

(When different fastening force is used)
When changing the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10, for example, when the fastening force of the first hydraulic clutch 9 is high and the fastening force of the second hydraulic clutch 10 is low, the switching valve 41 is set to the first. 2, the oil pump 13 is driven and its discharge pressure is adjusted to a desired pressure required by the first hydraulic clutch 9, and the pressure regulating valve 14 is driven and its output pressure is adjusted by the second hydraulic clutch 10. Depressurize to the desired pressure required.

  As a result, as shown in FIG. 13, the discharge pressure of the oil pump 13 is supplied to the first hydraulic clutch 9 as the operating pressure, and the output pressure of the pressure regulating valve 14 is supplied to the second hydraulic clutch 10 as the operating pressure. Therefore, the fastening force of the first hydraulic clutch 9 can be increased and the fastening force of the second hydraulic clutch 10 can be reduced.

(When switching fastening force)
When switching the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 from the state of FIG. 13, the switching valve 41 is switched from the second state to the first state. At this time, as shown in FIG. 15, the second oil passage 22 and the fourth oil passage 24 communicate with each other via the path 42b, and the first oil path 21 and the third oil path 23 communicate with each other via the path 42a. Therefore, the discharge pressure of the oil pump 13 is supplied to the second hydraulic clutch 10 via the fourth oil passage 24, and the output pressure of the pressure regulating valve 14 passes from the oil passage 25 via the third oil passage 23. And supplied to the first hydraulic clutch 9.

  As a result, from the state where the fastening force of the first hydraulic clutch 9 is high and the fastening force of the second hydraulic clutch 10 is low, the fastening force of the first hydraulic clutch 9 is low and the fastening force of the second hydraulic clutch 10 is high. And can be switched instantly.

(Fastening force retention)
When the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 is maintained, the third oil path 23 and the fourth oil path 24 are not in communication with any path (third state). The switching valve 41 is operated. Thereby, since the hydraulic pressure supplied to both hydraulic chambers 9a and 10a is maintained, the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 can be maintained.

(Average fastening force)
When the fastening forces of the first hydraulic clutch 9 and the second hydraulic clutch 10 are averaged from the state where the fastening forces of the first hydraulic clutch 9 and the second hydraulic clutch 10 are made different, the third oil passage 23 and the fourth oil The switching valve 41 is operated so as to be in a state (fourth state) in which the path 24 communicates with the path 42c or the path 42d. Thereby, since the hydraulic pressure supplied to both hydraulic chambers 9a and 10a is averaged, the fastening force of the first hydraulic clutch 9 and the second hydraulic clutch 10 can be instantaneously made equal.

  Therefore, the hydraulic clutch control device according to the third embodiment can achieve the same effects as those of the second embodiment.

(Other examples)
The best mode for carrying out the present invention has been described based on the first to third embodiments. However, the specific configuration of the present invention is not limited to the first to third embodiments. Design changes and the like within a range that does not depart from the gist are also included in the present invention.

  For example, the spool type switching valve is used as the switching valve in the first embodiment, and the rotary switching valve is used as the switching valve in the second and third embodiments. However, the structure of the switching valve is arbitrary, and is at least in the first state. And the second state may be switched.

  In the switching valve 41 of the third embodiment, the path 42a and the path 42b of the valve main body 42 are arranged with the height shifted from each other. However, as shown in FIG. 16, only the interfering portion is arranged with the height of the path 42a shifted. The opening portion may have the same height as the other paths 42b, 42c, and 42d.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an overall configuration diagram showing a drive system of a rear wheel drive vehicle to which a hydraulic clutch control device of Embodiment 1 is applied. FIG. 3 is a diagram illustrating a configuration of a control valve unit 11 according to the first embodiment. It is a figure which shows the state of the switching valve 15 in case the fastening force of two clutches is made the same. It is a figure which shows the state of the switching valve 15 in the case of making the fastening force of a 1st hydraulic clutch high and making the fastening force of a 2nd hydraulic clutch low. It is a figure which shows the state of the switching valve 15 in the case of making the fastening force of a 1st hydraulic clutch low and making the fastening force of a 2nd hydraulic clutch high. FIG. 6 is a diagram illustrating a configuration of a control valve unit 30 according to a second embodiment. It is a figure which shows the shape of the valve body 32 of Example 2. FIG. It is a figure which shows the structure of the switching valve 31 of Example 2. FIG. It is a figure which shows the state of the switching valve 31 in the case of making the fastening force of a 1st hydraulic clutch high and making the fastening force of a 2nd hydraulic clutch low. It is a figure which shows the state of the switching valve 31 in case the fastening force of a 1st hydraulic clutch is made low and the fastening force of a 2nd hydraulic clutch is made high. It is a figure which shows the state of the switching valve 31 in the case of hold | maintaining the fastening force of a clutch. It is a figure which shows the state of the switching valve 31 in the case of averaging the fastening force of a clutch. It is a figure which shows the structure of the control valve unit 40 of Example 3. FIG. It is a figure which shows the shape of the valve body 42 of Example 3. FIG. It is a figure which shows the state of the switching valve 41 in the case of making the fastening force of a 1st hydraulic clutch low and making the fastening force of a 2nd hydraulic clutch high. It is a figure which shows the shape of the valve | bulb main body of another Example.

Explanation of symbols

1 Engine 2 Automatic transmission 3 Propeller shaft 4 Differential gears 5 and 6 Left and right drive axles 7 and 8 Left and right rear wheels 9 Torque transmission clutch (first hydraulic clutch)
10 Torque transmission clutch (second hydraulic clutch)
9a, 10a Hydraulic chamber 11 Control valve unit 12 Controller 13 Oil pump 13a Discharge port 13b Electric motor 14 Pressure regulating valve 14a Input port 14b Output port 15 Switching valve 16 Pump discharge oil passage 17 Valve housing 17a First input port 17b Second input port 17c 1st output port 17d 2nd output port 17e 3rd output port 18 Spool 19 Solenoid 20 Spring 21 1st oil path 22 2nd oil path 22 'Oil path 23 3rd oil path 24 4th oil path 25 Oil path 30 Control Valve unit 31 Switching valve 32 Valve bodies 32a to 32e Path 33 Stepping motor 40 Control valve unit 41 Switching valve 42 Valve bodies 42a to 42d Path

Claims (7)

An oil pump,
A pressure regulating valve for regulating the input hydraulic pressure to a desired pressure;
A pump discharge oil passage communicating the discharge port of the oil pump and the input port of the pressure regulating valve;
A first oil passage communicating with the output port of the pressure regulating valve;
A second oil passage communicating with the pump discharge oil passage;
A third oil passage communicating with the hydraulic chamber of the first hydraulic clutch;
A fourth oil passage communicating with the hydraulic chamber of the second hydraulic clutch;
A first state for maintaining communication between the first oil passage and the third oil passage and communication between the second oil passage and the fourth oil passage; and the first oil passage and the fourth oil passage. A switching valve capable of switching between a second state that maintains communication with the second oil passage and the communication between the second oil passage and the third oil passage;
Control means for changing the discharge pressure of the oil pump, the output pressure of the pressure regulating valve and the state of the switching valve, and controlling the fastening force of the first hydraulic clutch and the second hydraulic clutch;
An apparatus for controlling a hydraulic clutch, comprising: The control apparatus for a hydraulic clutch according to claim 1,
The control device for a hydraulic clutch, wherein the switching valve can be switched to a third state in which the third oil passage and the fourth oil passage are respectively shut off. The control apparatus for a hydraulic clutch according to claim 1 or 2,
The control device for a hydraulic clutch, wherein the switching valve is switchable to a fourth state in which communication between the third oil passage and the fourth oil passage is maintained. The hydraulic clutch control device according to any one of claims 1 to 3,
A control device for a hydraulic clutch, wherein the switching valve is a spool type switching valve. The control apparatus for a hydraulic clutch according to claim 4,
The spool type switching valve is
A first input port connected to the first oil passage;
A second input port connected to the second oil passage;
A first output port connected to the third oil passage;
A second output port connected to the fourth oil passage;
A third output port connected to the third oil passage;
The first state corresponding to the first state in which the communication between the first input port and the first output port, the communication between the second input port and the second output port, and the closing of the third output port are maintained. The second position maintaining the spool position, the communication between the first input port and the second output port, the communication between the second input port and the third output port, and the closing of the first output port. A spool that switches between a second spool position corresponding to the state of
An apparatus for controlling a hydraulic clutch, comprising: The hydraulic clutch control device according to any one of claims 1 to 3,
A control device for a hydraulic clutch, wherein the switching valve is a rotary switching valve. In the control apparatus of the hydraulic clutch according to any one of claims 1 to 6,
The first hydraulic clutch and the second hydraulic clutch are torque transmission clutches that transmit power from a power source to left and right drive wheels,
The control means changes a discharge pressure of the oil pump, an output pressure of the pressure regulating valve, and a state of the switching valve based on a required driving force difference set according to a running state. Control device.

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