JPS647247B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a hydraulic clutch attached to an internal combustion engine, etc., by controlling the hydraulic pressure according to the engine rotation speed, thereby eliminating the delay in the time required for fitting, and reducing the shock at the time of fitting. This invention relates to a control device that eliminates the problem and allows smooth insertion.

For example, an internal combustion engine such as a marine diesel engine is usually equipped with a deceleration/reversal device consisting of a combination of a hydraulic clutch and a speed change gear between the engine output shaft and the propeller shaft, and a hydraulic directional changer and hydraulic adjustment device. By controlling the direction and degree of engagement of the hydraulic clutch, the direction and speed of rotation of the propeller shaft can be adjusted to freely control forward, reverse, speed, etc. of the ship.

By the way, in this type of device, if the hydraulic pressure is maintained at a high pressure when the clutch is in the neutral position, there will be no delay in the engagement time when the clutch is operated, but on the other hand, the shock at the time of engagement will be large, and conversely, if the hydraulic pressure is maintained at a high pressure when the clutch is in the neutral state, the hydraulic pressure will be kept at a low pressure. If it is held, there is a general property that the fitting shot becomes smaller but the fitting time is delayed, and in either case there is a problem that the feeling during operation becomes poor. For this reason, attempts have been made to use a slow-fitting valve that applies a pressure regulating valve structure to perform the fitting operation while lowering the pressure when the hydraulic circuit for clutch fitting is formed. As a result, the insertion time becomes relatively long, and the intended purpose of not delaying the insertion time and eliminating the insertion shot could not be fully achieved.

The present invention has focused on the above-mentioned problems, and an object of the present invention is to provide a control device for a hydraulic clutch that can smoothly engage the clutch by preventing shock during engagement without delaying the engagement time during clutch operation. A clutch hydraulic directional switch which can be driven electrically, a hydraulic pressure adjusting device which can be adjusted to any pressure, and a hydraulic pressure detector,
The present invention is characterized in that it includes an engine rotation speed detector, a control section that provides control outputs to the clutch hydraulic pressure direction changeover device and the hydraulic pressure adjustment device, and that the control section is provided with the following calculation means. When the clutch is in neutral, the calculation means provided in the control section outputs a control output to the hydraulic pressure adjustment device to maintain the neutral pressure preset according to the engine speed, and also controls the operation of the clutch hydraulic directional switch. When a hydraulic circuit is formed on the side where the clutch engages, the neutral pressure is maintained for a predetermined pressure reduction waiting time according to the engine speed, and then the hydraulic pressure is increased to a predetermined pressure that suppresses the engagement shock to an allowable value. A control output that lowers the pressure of the clutch is output to the hydraulic adjustment device, and after maintaining the low predetermined pressure for a preset pressure increase waiting time, a control output that increases the hydraulic pressure to a relatively high clutch engagement setting pressure is output to the hydraulic pressure adjustment device. It is configured to output to a regulating device. The neutral pressure and depressurization waiting time, which are set according to the engine speed mentioned above, are both determined through tests, and this changes the hydraulic oil discharge amount and pressure, which changes the engine speed. This makes it possible to perform appropriate control that deals with the fact that the actual oil pressure changes with respect to the set value depending on the rotational speed. In addition, the low predetermined pressure that allows the above-mentioned insertion shock to be kept within an allowable value, the pressure increase waiting time, and the clutch insertion setting pressure after pressure increase are determined by the clutch model and capacity, and these are also determined by tests in advance. This is what is required.

Hereinafter, the present invention will be specifically explained with reference to an illustrated embodiment.

In the block diagram of FIG. 1, 1 is a clutch hydraulic pressure direction switch, 2 is a hydraulic pressure adjusting device consisting of a hydraulic pressure regulating valve 3 and a drive device 4 that drives it, 5 is an oil pressure detector, 6 is an engine rotation speed detector, 7 is a control section. The control unit 7 receives manual input such as steering wheel operation.
A/D converter 9 converts the input from the oil pressure detector 5 into A/D, and a relay 1 provides a drive output to the drive device 4.
0, 11, memory device 12, and various input signals to perform necessary calculations and output a control output for the clutch hydraulic directional switch 1 and a control output of the hydraulic pressure adjustment device 2 for the relays 10, 11. It is equipped with a device 13, the main parts of which can be configured by, for example, a microcomputer.

FIG. 2 shows an example of a schematic structure of the clutch hydraulic direction changer 1 and the hydraulic pressure adjusting device 2, and a related hydraulic circuit. A DC motor 4a is used in the drive device 4 of the hydraulic adjustment device 2, and a relay 10
Alternatively, the output shaft 21 rotates in the direction of pressure increase or decrease in response to the operation of 11, and the servo valve 23 in the oil pressure regulating valve 3 is moved in the axial direction via the threaded coupling 22. Accordingly, the servo valve 23
The servo piston 24 provided on the outside moves to a position where the repulsive force of the pressure regulating spring 25 and the supply pressure of the hydraulic pump 26 are balanced, and the pressure regulated to a predetermined value is supplied to the output port 27. be done. A potentiometer 5a is used in the oil pressure detector 5, and is configured to detect the position of a detection guide pin 28 attached to the shaft of the servo valve 23. There is a unique relationship between the reading of the potentiometer 5a and the pressure obtained at the output port 27 of the hydraulic pressure regulating valve 3, as shown in FIG. Then pressure is detected and the potentiometer 5
The reading of a is sent to the arithmetic unit 13 via the A/D converter 9.
is input.

The clutch hydraulic directional switch 1 is connected to a pilot valve 3.
1. It is equipped with a forward switching valve 32 and a reverse switching valve 33, and the figure shows a neutral state. Arithmetic device 1
When the pilot valve 31 operates to the forward or reverse side according to the output of the hydraulic pressure regulating valve 3, the valve body 34 or 35 of the switching valve 32 or 33 moves due to the supply pressure of the hydraulic pump 26, and the output port 27 of the hydraulic pressure regulating valve 3 moves.
A hydraulic circuit is formed from the clutch to the forward cylinder 36 or reverse cylinder 37, and the clutch is inserted into the forward or reverse side.

Note that 38 is a filter, 39 is a pressure regulating valve, and 40 is an oil pan.

Next, the operation will be explained. First, when the clutch is in the neutral state, no pressure is supplied to the forward cylinder 36 and the reverse cylinder 37, and the pressure obtained at the output port 27 is closed before the switching valves 32 and 33. At this time, the hydraulic pressure adjustment device 2 maintains the neutral pressure P ₀ at a relatively high pressure with the servo valve 23 pushed in the pressure increasing direction. This neutral pressure P ₀ is set according to the engine speed as shown in Figure 4, and there is a relationship in which the pressure increases as the engine speed decreases, and this relationship is It is stored in the storage device 12 in the form of a table. Then, the arithmetic unit 13 performs an arithmetic operation to obtain a reading of the potentiometer 5a that satisfies the relationship shown in FIG.
The DC motor 4a is driven and the hydraulic pressure adjustment device 2 is controlled to obtain a predetermined neutral output _P0 .

Now, manually operate the clutch position changeover switch 8.
When the switch 8 is operated, the arithmetic unit 13
A switching signal is input from the arithmetic unit 13, and a control output corresponding to the switching signal is outputted from the arithmetic unit 13 to the clutch hydraulic pressure direction switching valve 1, and the switching valve 32 or 33 is operated to start the clutch engagement operation. Next, after waiting for a pressure reduction waiting time T ₂ corresponding to the engine speed, a control output is output that activates the relay 11 to operate the hydraulic pressure adjustment device 2 in the pressure reduction direction, and the potentiometer is increased to a preset low pressure P ₂ . Reduce the oil pressure while comparing the reading on the meter 5a. This decompression waiting time
T ₂ is set according to the engine speed as shown in Figure 5, and the relationship is such that the time becomes longer as the engine speed decreases, and this relationship can be expressed in the form of a numerical table. It is stored in the storage device 12.
Then, the calculation device 13 calculates a time T ₂ that satisfies the relationship shown in FIG. 5 in accordance with the detection output from the engine speed detector 6, and starts the operation of the relay 11. In addition, the low pressure _P2 is a value obtained in advance according to the clutch capacity, etc., and is a pressure that maintains the half-clutch state so that the rotational transmission rate does not become too small and the shock is small. It is stored in the device 12.

Once the pressure P ₂ is obtained, this pressure P ₂ is maintained for a pressure increase waiting time T ₃ , and then a control output for activating the relay 10 is output from the calculation device 13, and the hydraulic pressure is increased to the clutch engagement setting pressure P ₁ . Rise. This pressure increase waiting time _T3 is intended to alleviate the shock by lengthening the rise time, and is a value obtained in advance according to the clutch capacity, etc., and is stored in the storage device 12. . Also the pressure
_P1 is the pressure at which the clutch can be reliably kept in the engaged state, and is obtained by multiplying the slip limit pressure of the clutch by a safety factor, regardless of the engine speed. Therefore, this pressure P ₁ is also a value obtained in advance according to the clutch capacity, etc., and the memory device 1
It is stored in 2.

FIG. 6 is a control flowchart for performing the above operations, and FIG. 7 is a time chart. Time T ₁ in Fig. 7 is the fitting time, and the driven shaft rotation speed, for example, the propeller rotation speed, rises over a rising time T ₄ after this fitting time T ₁ , and operation at the desired speed is started. However, the above-mentioned depressurization waiting time T ₂ does not require delaying the fitting time T ₁ by maintaining a relatively high neutral pressure P ₀ for a certain period of time, and moreover, the driven shaft rotation speed is reduced in relation to the pressure P ₂ . The optimum value is set according to the engine speed so that the start-up is smooth and there is no jamming shock. Time _T'4 in FIG. 7 is the rise time of the driven shaft rotational speed when such hydraulic control is not performed, and shows that the rise is rapid and the shock is large.

In addition, when the engine speed is above a certain value, that is, when it is above ₈₀₀ rpm in the examples shown in _Figs . A pressure reduction to pressure P ₂ takes place immediately. This is because at 800rpm or more, there is sufficient discharge, so if the oil pressure is set above a certain value, the insertion time will hardly change even if the waiting time is set to zero and the above operation is performed. It is.

As is clear from the description of the embodiments above, the present invention maintains a neutral pressure that is preset according to the engine speed when the clutch is in its neutral state, and maintains a neutral pressure that is preset according to the engine speed when the clutch is engaged. After maintaining the neutral pressure for the decompression waiting time,
The hydraulic pressure is lowered to a predetermined pressure that keeps the engagement shock within the allowable value, and after a preset pressure increase waiting time, the oil pressure is increased to the clutch engagement setting pressure, reducing the delay in clutch engagement time. In addition to minimizing the hydraulic pressure, it is possible to reduce the shock when the clutch engages by lowering the oil pressure. Moreover, these controls compensate for changes in the hydraulic oil discharge amount and actual oil pressure depending on the engine speed. However, it becomes easy to always perform good control regardless of the engine speed. In addition, the actual operation of manual clutch switching is completely unchanged from conventional methods, and operability is not compromised.Since the entire device can be controlled electrically, remote control becomes easier and operability can be improved. It is.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention; Fig. 1 is a block diagram, Fig. 2 is a hydraulic system diagram showing the schematic structure of the hydraulic circuit and related equipment, and Fig. 3 is the relationship between potentiometer reading and oil pressure. Figure 4 is a diagram showing the relationship between engine speed and neutral pressure set value, Figure 5 is a diagram showing the relationship between the engine speed and the set value of neutral pressure.
The figure shows the relationship between the engine speed and the set value of the depressurization waiting time, Figure 6 is the control flowchart, and Figure 7
The figure is a control time chart. DESCRIPTION OF SYMBOLS 1...Clutch oil pressure direction changer, 2...Hydraulic pressure adjustment device, 5...Oil pressure detector, 6...Engine speed detector, 7...Control unit, 13...Arithmetic unit, _P0 ...
...neutral pressure, P ₂ ...low pressure, P ₁ ...clutch engagement setting pressure, T ₂ ...pressure reduction waiting time, T ₃ ...
Pressure increase waiting time.

Claims (1)

[Scope of Claims] 1. An electrically driveable clutch hydraulic direction changeover device, a hydraulic pressure adjustment device that can be adjusted to any pressure, a hydraulic pressure detector, an engine rotation speed detector, and the clutch hydraulic direction changeover device. In a hydraulic clutch control device that is equipped with a control unit that provides a control output to a hydraulic adjustment device, when the clutch is in neutral, a control output is sent to the hydraulic adjustment device to maintain a neutral pressure that is preset according to the engine speed. When a hydraulic circuit is formed on the side where the clutch engages due to the operation of the clutch hydraulic direction switch, the neutral pressure is maintained for a pressure reduction waiting time preset according to the engine speed, and then A control output is output to the hydraulic pressure adjustment device to reduce the hydraulic pressure to a predetermined pressure that suppresses the engagement shock to an allowable value, and after maintaining the low predetermined pressure for a preset pressure increase waiting time, a relatively high clutch pressure is applied. 1. A control device for a hydraulic clutch, characterized in that the control section is provided with arithmetic means for outputting a control output for increasing the hydraulic pressure to a setting pressure for fitting to a hydraulic pressure adjusting device.