JPS62105796A - Trawling device for ship - Google Patents

Abstract

PURPOSE:To enable quiet trawling by keeping hydraulic pressure delivery to a hydraulic clutch lower than a hydraulic pressure upper limit in the upper limit range of outputted number of revolutions for trawling. CONSTITUTION:A control circuit 17 when a control means '9' carries out an intensifying control, makes judgement on an upper limit judgement means 'l'as to whether a hydraulic pressure value detected by a detecting means 'j' exceeds the upper limit of hydraulic pressure for trawling in a memory means 'k' corresponding to the outputted number of revolutions from a detecting means 'h'. If said hydraulic pressure value is over the upper limit, an intensification- killing means 'm' stops a further intensifying operation on a pressure regulation means 'f'. Also, when a lower limit value judgement means 'n' has found that the set value of the outputted number of revolutions on a setting means 'C' is below a lower limit for enabling trawling, an intermittent boosting means 'o' causes the regulated pressure on a pressure regulation means 'f' for a hydraulic clutch 'e' to fluctuate alternately into hydraulic pressure permitting a half- released clutch and a fully released clutch, thereby enabling a less noisy and extremely low speed trawling operation.

Description

[Detailed Description of the Invention] Technical Field> The present invention is applicable to ships such as ifrt ships and work boats.
Regarding the filtration device.

<Prior art> Vessel trawling devices are used when fishing boats are trolling or when work boats are trolling against the current. When working by stopping at a fixed point in the sea 1-1. III FT: By controlling the hydraulic pressure supplied to the clutch, the clutch friction plate is made to slither and 'I! It is used to reduce the rotation speed of the novella to a lower speed than the normal speed by the reduction ratio of the clutch and the rotation speed of the engine, and to keep it at a very low speed. be.

By the way, as this type of device, for example, Japanese Patent Application Laid-open No.
As described in Publication No. 160/129, the number of revolutions of the propeller shaft is detected, this number of revolutions is compared with a preset value, the deviation is calculated, and the difference between the engine drive shaft and the propeller shaft is determined. By increasing/decreasing the hydraulic pressure applied to a hydraulic clutch interposed between the two in accordance with the deviation, the clutch is brought into the required half-clutch state and the rotational speed of the propeller shaft is controlled to the required low speed. Shino has already been proposed.

In such a device, as mentioned above, when the hydraulic clutch is 100% engaged, the propeller rotation speed (output rotation speed) Np is equal to the engine rotation speed Ne, which is the input rotation speed, and the reduction ratio l. (N p= N e/
i) Assuming that the rotational speed is a steady rotational speed, in the case of trolling, an output rotational speed lower than the steady rotational speed is achieved by making the engaged state of the hydraulic clutch less than 100%.

However, if the rotational speed is less than the steady rotational speed, the output rotational speed will be reduced to 1' clutch. It's not a translation.

The inventor carried out various measurements [2] and found that the output rotational speed that can be achieved with a half-clutch has an upper limit and a lower limit in the region below the steady rotational speed, and each has its own special problems. be.

The diagram in FIG. 5 shows the relationship between the input rotational speed Ne and the output rotational speed NI). In the figure, power is taken out to the symbol 'i'i
This is the lowest input rotation speed that is possible for a clutch, and the highest input rotation speed that is possible for a 3 or half-clutch; anything above that is a dangerous area for trolling. The slope l indicates the reduction ratio, and this reduction ratio i is obtained by 100% engagement of the A1j pressure clutch. The area between the input rotational speeds A and B where the slope is less than or equal to the slope I is the area to be subjected to trolling control.

Now, the area of input rotation speed where trolling is possible A - [
(Within this range, when the engagement rate of the hydraulic clutch is 70%, there is a limit value of the oil pressure supplied to the hydraulic clutch, and when the oil pressure increases slightly above that value, the hydraulic clutch suddenly reaches 100%.) There is a fact that it moves into a state of being stuck.

However, the L limit value Pu of the oil pressure is not a constant value,
As shown in the diagram of FIG. 6, it changes depending on the input rotational speed NQ.

Therefore, if trolling control is performed when the clutch is occupied at around 70%, the hydraulic clutch may become completely engaged and the rotational speed of the bellows may drop, causing shock to the hull. , East was uncomfortable and 4-ro.

In addition, in an attempt to avoid such inconvenience through operator operations, the range of the output rotation speed Np that can be set varies widely depending on the input rotation speed Ne, as shown in FIG. Avoidance operations are not easy, and in reality, settings may be made beyond the possible setting range, in which case,
The propeller rotation speed increases rapidly, causing a shock to the hull.

Furthermore, in the lower limit range of the output rotation speed Np that can be set for trolling, the lower limit value Pd of the oil pressure that can be half-clutched is (
j (1,L) When the hydraulic pressure falls below this pressure, power transmission by the hydraulic clutch is no longer performed, and the propeller rotation stops.

The fjth limit of this i+b pressure]d is determined by the characteristics of the power transmission section, and is constant at -, regardless of the input rotational speed Ne. Therefore, corresponding to the lower limit value I) (1 of the oil pressure, '4t, the output rotation speed Np that can be realized by the clutch
The F limit value Npd (shown in FIG. 5) remains constant regardless of the input rotational speed Nc.

In response to this kind of problem, it may be better not to lower the oil pressure below the lower limit value Pd, or in reality, in CI,
Corresponding to this oil pressure lower limit value Pcl, ) tU -II
An even lower speed is required due to the song rating.

Therefore, in order to achieve the above-mentioned low slow speed, a method has been considered in which the ship's large inertia is used to alternately rotate and stop the propeller. (Tokuko Chu 1 ton, 1987-2807).

However, if the propeller is driven to rotate intermittently as described in 1-, a large shock will be applied to the hull, and there is a risk that the speed of the propeller will become too low during rotation.

<Object of the Invention> The present invention has been made in view of two problems, and aims to eliminate the inconveniences occurring in the I-range and lower limit range of the output rotation speed for trolling, and to improve riding comfort. The purpose is to improve the performance of the vehicle and to realize even lower slow speeds than before without any problems.

<Structure of the Invention> In order to achieve the above object, the present invention provides an output rotation speed detection means for detecting the rotation speed of the propeller a, as shown in the functional block diagram of FIG. Set 4
a hydraulic clutch C interposed between the engine d and the propeller a; and an electrical pressure regulating means f for increasing or decreasing the nb pressure supplied to the nb indenter latch. and a control means g that compares a set value and a detected value of the output rotation speed and causes the pressure adjustment means f to increase or decrease the pressure based on the deviation, in which the rotation speed of the engine d is detected. an input rotation speed detection means ri; a hydraulic pressure detection means j for detecting the hydraulic pressure supplied to the hydraulic clutch e;
The 11 limit value of the oil pressure for l-Rollin' corresponding to the input rotation speed is memorized, and when the control means g performs pressure increase control, the detected oil pressure value at that time is the input rotation speed. an upper limit judgment means ρ which determines whether or not the hydraulic pressure exceeds the limit value, and a pressure regulating means r which determines whether the detected value exceeds the upper limit value 1-
pressure increase avoidance means m for stopping the pressure increase operation; and F limit value determining means for determining whether the set value of the output rotation speed is within the F limit value of the output rotation speed that allows trolling (F times -). n and the set value of the output rotation speed are 1; an intermittent pressurizing means that alternately changes the pressure regulation by the pressure regulating means r to a hydraulic pressure that enables half-clutching and a hydraulic pressure that disengages the clutch; A trolling device for a ship was constructed by including 0 and 0. In FIG. 1, p+ and tib are pressure sources.

<Example> The present invention will be described in detail below based on an example shown in the drawings. FIG. 2 is an overall configuration diagram of the device of the present invention, in which reference numeral 1 is an engine, 2.3 is a surface-pressure friction type for forward and reverse movement, respectively, 4 is a propeller, and 4 is a propeller gear. 6, an output rotation sensor (for example, an electromagnetic pickup) 7, which is output rotation speed detection means for detecting the rotation speed of the propeller sleeve 5, is provided. Also, the engine
An input rotation sensor 8 is provided on the drive shaft as input rotation speed detection means. 9 is a reverse switching valve 11, and through the switching valve 9, the pressure i+I+ from the 11] pump lO is
In the forward hydraulic clutch 2, the hydraulic clutch 2 is selectively supplied to either one of the reverse hydraulic oil 1 and the hydraulic clutch 3. An electrical pressure regulating means 11 is interposed in the hydraulic path between the switching valve 9 and the hydraulic pump 10. In this embodiment, the j41E means 11 is composed of a motor 12, a servo valve 13 operated by the drive of the motor 12, and a pressure reducing valve 14 interlocked with the servo valve 13. 1
Reference numeral 5 denotes a position sensor as a hydraulic pressure detection means for detecting the hydraulic pressure supplied to the #l11 pressure cylinders 2 and 3.
By detecting 1, the oil pressure is indirectly detected. 1G is an output rotation speed setting device for setting the rotation speed of the propeller sleeve 5; 17 is an output rotation speed setting device for controlling the drive of the motor 12, and a core A1 pressure means 111. X place 'M (h: J, 'a pressure cutting operation t) N mouth ib'j fl1 circuit, 18 is JAI
19 is a pressure valve, 20 is a lubricant, and 111 is a cooler.

The control circuit 17 controls the first
In the control means g and storage means shown in the figure, the -1-limit judgment p stage Q, the pressure increase avoidance means m, and the lower limit value? -11 Since the valley function of the constant means n and the intermittent pressurizing means 0 has been determined, the circuit (1) is shown in Figure 3 as shown in Figure 4-1. 1 control circuit I7 has CP Ll 21 , LE Oλ422
,! M23, A, / I) Converter: 24,
Counter 25, waveform adjustment circuit 26, drive control section 27
Ohageden i! ri circuit 28. The A/D converter 24 is connected to the output horn rotation speed setting device 16 and the position sensor→)l
The setting value signal from the setting device 16 and the oil pressure detection signal from the position sensor 15 are connected to the digital 11.
The waveform shaping circuit 2G prepares the rotation detection signal wave j[': from the output rotation centimeter 7 and the input rotation sensor 8 and outputs it to the counter 25. The counter 25 counts the waveform-adjusted 3-rotation detection signal, and the drive side 111is 27 supplies electricity 11;(from the battery 29 to the motor 12 in response to a command signal from the CPU 2l).゛Lo.

Next, the control operation of the control circuit 17 will be explained using the flowchart shown in FIG. In S2, it is determined whether the set value Nps is within a predetermined trolling range or exceeds the predetermined range.Set value Np
If s exceeds a predetermined range, trolling is not performed, so the process moves to step S3, and the drive control section is set to maximize the hydraulic pressure supplied to the hydraulic clutch 2.3 in step S3. A command signal is output to 27. This causes the motor 12 to open the pressure reducing valve 14 to open the M1! Increase the oil pressure supplied to the pressure terraces 2 and 3 U-
The pressure reducing valve 14 is fully opened. When this step S3 is completed, step S
Return to 1.

When the set value Nps is within the predetermined trolling range, the trolling control from step 84 onwards is entered. ×→・
Lee'S・l r; L"C is 1.1ji constant 1 □ straight Jl)
S!・I: 1i no 9 set & 0) T” limit &t N p
cl から') -i'47) roh fika &f cut・)
It's true. If the setting value N1) S or 1:' limit (lI't\pd is reached and L'i; is not reached, the process will proceed to Step 711 No. 10.
If the setting point Nps is less than the lower limit value Npd, the steering wheel and knob S should be adjusted from step S5 to achieve low speed.
Enter the routine of intermittent pressurization up to 9.

That is, in step S5, the motor 12 is first driven in the opening direction, and the pressure of the pressure regulating stage 11 is set to a hydraulic pressure Pa that allows the pressure adjustment stage 11 to reach the maximum pressure. 12 in the direction of the closing force, change the pressure of the pressure regulating means 11 to the oil pressure 1) li at which the clutch is turned off, 5, wait for the required time in step S8, 2, and step S9.
At 41 (determine the number of times of pressure transformation history, if the number of times does not reach a predetermined number of times, return to step S5, but if it reaches a predetermined number of times, return is reached.

In this way, since hydraulic pressure is applied to the hydraulic clutch 2 and 3 intermittently to enable half-clutching, the Ura 111E tarlage 2.3 is intermittently in a half-clutching state, thereby realizing a low and slow rotation of the propeller 4. ΔRero.

In step S4, the set value Nps is the lower limit value N1)
(If it is 1, the process goes to step S10. 3, and in step S12, the absolute value of this difference dN is calculated within a predetermined tolerance fi.
! It is determined whether or not the value is larger than 7'l (5 in this embodiment). If this judgment is NO, that is, if the difference (IN) falls within the range of the predetermined tolerance g((A), there is no need to operate the pressure reducing valve 14, and the process returns.

If the difference dN exceeds the range of the predetermined allowable ff1A, in step S13, the difference (motor drive amount corresponding to IN, that is, 1!1X electric time T to the motor 12,
Calculate np. Then, in the next step S14, the difference d
Determine whether N is +H or a negative pawl 3. If the difference dN is positive jl and yes 1, then the rotation speed Nl) or the set value Nps is exceeded, so go to the hydraulic clutch 2゜3. Is it necessary to reduce the supply oil pressure? In that case, proceed to step S15, drive the motor 12 in the closing direction with the knob S15, close the 1st 14, and move on to the hydraulic crank !2 and 3. The pressure is reduced at +111'lli.This results in a half-clutch state that is shallower than the hydraulic pressure '7' and '7'. 4-ro.

Based on step S Ill, the difference dN or negative l
il, the output rotational speed Np does not exceed the set value Nps, so it is necessary to increase the pressure supplied to the hydraulic clutches 2 and 3-\.In the present invention, the output rotation speed Np does not exceed the set value Nps. Then, the hydraulic pressure is increased by 1,000 yen.

The routine from step S17 to step S20,
This is a routine for reducing the supply oil pressure from 1 to 1 to avoid pressure increase beyond the limit value PU. In Ste-Tsub S17, the height rotation v1. Ne is read, and at snap S18, the value for the supplied tune is taken by one through the position sensor 15.

Then, in step S19, from II O\422 to the input rotation speed N(!) corresponding to the detected value of
Lil,! Search for value P u (2, corresponding 10 limit value 1) I”
and the detected value 1, and it is determined whether the detected value of the oil pressure is within the upper limit value Pu. If the detected oil pressure value exceeds the L limit value Pu, further pressure increase will cause 111
Since there is a risk that the pressure clutch 2.3 may shift to the 100% 1 assignment state all at once, it is necessary to avoid pressure increase. Therefore, in step S20), the drive of the motor 12 is stopped, and further pressure increase by the pressure regulating means II is stopped.
It's true. During trolling control, the hydraulic pressure is never increased beyond the limit value Pu, so there is no risk that the hydraulic clutch 2.3 will be completely engaged inadvertently.

If it is determined in the step S19 that the detected value of the oil pressure is within 1 - the limit value []U, in that case, the oil pressure will be increased to avoid problem B, so the process moves to step S2+, and in step S2+, the motor 12 to rotate in the opening direction, thereby driving the pressure reducing valve 14 in the increasing pressure direction, increasing the oil pressure to the hydraulic clutch 2.3, and determining the elapse of the energization time Tnp in step S22. do.

When the pressure increase or decrease by the pressure regulating means 11 is completed, i.e. step S16 or step S22 is completed, the steno knob! ; Proceeds to step 23, waits for a certain period of time (5 (.I.) in this embodiment), and returns after this waiting time has elapsed.

(Summary of the invention) 2 As shown in [-], the present invention maintains the hydraulic pressure supplied to the hydraulic clutch below the upper limit of the hydraulic pressure in the -L dual-lens range of the output rotation speed for trolling. During the J-ring control, there is no risk of the hydraulic clutch accidentally pulling in completely and causing turbulence to the hull, and quiet trolling is possible.

Above, in the 1.5 range of output rotation speed for trolling, the 411 clutch is in a clutch state intermittently due to the MI+ pressure that is applied intermittently, so this intermittent 11', depending on the clutch state, a low slow speed with a low upward speed can be realized.

Moreover, in that case, the power transmission to the propeller is not directly interrupted, but the pressure applied to the hydraulic clutch is interrupted.
Since the power transmission to the propeller is indirectly adjusted, the propeller rotation speed changes smoothly, causing a shock to the hull! There is no risk of the ship moving too far or moving too far.

[Brief explanation of drawings]

Figure 1 is a functional block diagram that clearly shows the configuration of the present invention, Figure 2 is a functional block diagram clearly showing the configuration of the present invention.
Figure 3 is a block diagram of the control circuit, Figure 3 is a block diagram of the control circuit, Figure 5 is a flowchart of the control operation, and Figure 5 is a line showing the relationship between input rotation speed and output rotation speed. 6 is a ten-line diagram showing the relationship between the input rotational speed and the two limit values of the oil pressure. l...engine, 2.3...hydraulic clutch, -propeller, 7.output rotation sensor, 8.input rotation sensor, 9.
・Front reverse switching valve, 11...Pressure adjustment stage, I2・Motor, 1
5. Position sensor (hydraulic pressure detection means), 16. Output rotation speed setting device, 17. Control circuit.

Claims (1)

[Claims] (1) An output rotation speed detection means for detecting the rotation speed of the propeller shaft, an output rotation speed setting means for setting the rotation speed of the propeller shaft, and a hydraulic clutch interposed between the engine and the propeller; It has an electrical pressure regulating means that increases or decreases the pressure supplied to the hydraulic clutch, and a control means that compares a set value and a detected value of the output rotation speed and causes the pressure regulating means to operate to increase or decrease the pressure based on the deviation. In a trolling device for a ship, input rotation speed detection means for detecting engine rotation speed, oil pressure detection means for detecting oil pressure supplied to a hydraulic clutch, and memory for storing an upper limit value of trolling oil pressure according to input rotation speed. means, upper limit determination means for determining whether or not the detected oil pressure value at that time exceeds the oil pressure upper limit value corresponding to the input rotational speed when the control means performs pressure increase control; pressure increase avoidance means that stops further pressure increase operation of the pressure regulating means when the pressure exceeds the limit value, and determines whether or not the set value of the output rotation speed is lower than the lower limit value of the output rotation speed that is possible for trolling. Lower limit value determining means, and intermittent pressurizing means for alternately changing the pressure regulation by the pressure regulating means to a hydraulic pressure that enables half-clutching and a hydraulic pressure that disengages the clutch when the set value of the output rotation speed is below the lower limit value. A vessel trolling device characterized by comprising: