JP3295471B2 - Hydraulic control mechanism of marine speed reducer - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed reducer for a marine vessel mounted on a ship, and more particularly to a control mechanism for hydraulic oil supplied to a hydraulic clutch provided in the speed reducer for a marine vessel.

[0002]

2. Description of the Related Art In a ship equipped with a marine deceleration reversing machine, the hydraulic clutch is maintained in a completely engaged state by continuously supplying high-pressure hydraulic oil to a selected forward or reverse hydraulic clutch. Thus, the engine torque input to the marine deceleration reverser is transmitted to the output shaft via the hydraulic clutch, and the propeller shaft connected to the output shaft is rotated to propel the hull. However, if the high-pressure oil is applied as it is immediately after the selection of the hydraulic clutch, a sudden fitting shock will occur. Conventionally, in order to prevent such a fitting shock, Japanese Patent Application Laid-Open
Techniques such as Japanese Patent Application Laid-Open No. 98744/1997, Japanese Utility Model Application Laid-Open No. 59-123000 and Japanese Utility Model Application Laid-Open No. 3-140660 are known.

[0003] However, in the prior art, an interlocking mechanism between the trolling valve and the operating hydraulic pressure adjusting valve is not provided. Therefore, when the trolling lever is suddenly operated from the trolling position to the fully engaged position of the hydraulic clutch, the hydraulic oil pressure rises rapidly in conjunction with the trolling lever, and the friction plate of the hydraulic clutch suddenly changes from a slip state to a slip state of zero. They are joined, causing a fitting impact, and suddenly starting. As a result, excessive torque is applied to the entire marine deceleration reversing machine, which leads to damage to the marine deceleration reversing machine.

[0004]

SUMMARY OF THE INVENTION The present invention relates to a trolling valve which lowers the operating oil pressure for pressing a hydraulic clutch friction plate of a marine deceleration reversing machine and makes the friction plate slip. By providing a position for communicating the back pressure valve of the operating hydraulic pressure adjustment valve to the drain circuit between the position of the slip 0 and the position of the trolling state, that is, the slip zone, when the lever is moved from the trolling position to the fully fitted position. Then, the operating oil pressure adjusted by the operating oil pressure adjusting valve is once maintained at a low pressure. Thus, even if the trolling lever is rapidly turned, the operating oil pressure adjusting valve is interlocked, so that no sudden increase in operating oil pressure occurs. As a result, the insertion impact can be reduced. In addition, excessive torque is not applied to the entire marine deceleration reversing machine, so that damage is avoided.

[0005]

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described. Claim 1 is a hydraulic circuit for a marine deceleration reversing machine, wherein the hydraulic circuit is a hydraulic oil pump P.
A trolling valve V2, a forward / backward switching valve V1, and a forward / backward clutch 3/4, with the forward / backward switching valve V1 in the forward or reverse direction,
2 was suddenly switched from the trolling position to the fully inserted position
When, in order to temporarily lower pressure hold hydraulic fluid pressure to be pressure regulated in work dynamic pressure regulating valve L1, the back chamber of the back chamber spool 5 for pressure regulation of the hydraulic pressure control valve L1, trolling valves V
2 and a pipe connected to the trolling valve V2.
Opening and closing the oil passage 30 of the pressure oil reaching the back chamber of the chamber spool 5
A rotary trolling lever spool 8 is provided.
Trolling for manually operating the spooling lever spool 8
The minimum trolling speed is achieved by turning the lever 1 at a certain angle.
During operation from the position to the fully inserted position
Trolling lever spoon on ring lever spool 8
Hole that connects the back chamber 31 of the pipe 8 to the drain communication oil passage d
S, and the drill hole S is provided between the trolling lever 1 and the trowel.
The rotation lever spool 8 rotates by a certain angle.
Before reaching full insertion, the drain communication oil passage d and the back chamber 31 are connected.
Trolling lever 1
When operating to the full insertion position, be sure to
The drain communication oil passage d communicates with the hydraulic pressure adjustment valve L1.
The chamber spool 5 is retracted to the lowest pressure position,
It is configured to delay the rise of the pressure oil thereafter .

According to a second aspect of the present invention, there is provided a hydraulic circuit for a marine deceleration / reversing machine, the hydraulic circuit comprising a hydraulic oil pump P, a trolling valve V2, a forward / reverse switching valve V1, a forward / reverse clutch 3.
・ For those equipped with 4, via trolling valve V2
Not directly from the hydraulic oil pump P to the forward / reverse switching valve V1
A circuit and throttle holes 7 are provided, and the forward / reverse switching valve V1 is
The trolling valve V2
Switch from the trolling position to the fully inserted position
In this case, the hydraulic oil pressure regulated by the hydraulic
In order to maintain a low pressure, the throttle of the forward / reverse switching valve V1 is reduced.
From the holes 7.7, the back pressure spool 5 of the hydraulic pressure control valve L1 is controlled.
A solenoid valve V3 is interposed in a circuit for supplying required pressure oil.
Backroom spool 5 for adjusting the pressure of operating hydraulic pressure adjustment valve L1
Is connected to the solenoid valve V3, and the other of the solenoid valves V3 is
It has a structure that communicates with the drain circuit D, and the trolling valve V2
Manual operation of the trolling lever spool 8 constituting
Trolling lever 1 and solenoid valve V3
Rolling valve V2 is completely inserted from trolling position
Of the part of the back room spool 5 during the moment before
Open solenoid valve V3 to drain circuit to reduce pressure to 0
The opening time of the solenoid valve V3 is determined by the timer T.
Is determined .

According to a third aspect of the present invention, there is provided a hydraulic circuit for a marine deceleration reverser, wherein the hydraulic circuit includes a hydraulic oil pump P and an operating oil pump.
Hydraulic pressure adjusting valve L1, electric pressure reducing valve or proportional solenoid valve V4, front
Hydraulic control with reverse switching valve V1 and forward / reverse clutches 3, 4
The trolling lever 1 or trolley
The operation of the dial 11 by the controller C
Then, when the forward / reverse switching valve V1 is completely and completely operated at once.
Electric pressure reducing valve or proportional
The magnetic valve V4 is connected between the hydraulic oil pump P and the forward / reverse switching valve V1.
Interposed, and the forward / backward switching valve V1 is operated forward or backward
In the state, when the electric pressure reducing valve or the proportional solenoid valve V4 is energized
By controlling the interval with the timer T, the operating oil pressure
The hydraulic oil pressure regulated by the regulating valve L1 is temporarily maintained at a low pressure.
It is a structure to make it.

[0008]

Next, the operation will be described. That is, even if the trolling lever is rapidly turned, the operating oil pressure adjusting valve is interlocked, so that no sudden increase in operating oil pressure occurs. As a result, the insertion impact can be reduced. In addition, excessive torque is not applied to the entire marine deceleration reversing machine, so that damage is avoided.

[0009]

Next, an embodiment will be described. FIG. 1 is a circuit diagram showing a hydraulic control mechanism of the first embodiment, FIG. 2 is a front sectional view of the trolling valve V2 of the first embodiment, FIG. 3 is a side view of the trolling valve V2, and FIG. FIG. 5 is a side view showing the operation state of the trolling lever spool 8 of FIG.
FIG. 6 is a front sectional view of the hydraulic pressure control valve L1, FIG. 6 is a hydraulic pressure rise curve diagram of the first embodiment, and FIG. 7 is a hydraulic pressure rise curve in a conventional hydraulic control mechanism of a marine deceleration reversing machine.

Referring to FIG. 1, a description will be given of a hydraulic control mechanism for a marine deceleration reverser according to the present invention. The inside of the marine deceleration reverser also serves as the hydraulic oil tank T. The hydraulic oil in the hydraulic oil tank T is pressurized by a hydraulic oil pump P,
The forward / backward movement is switched by a forward / backward switching valve V1 via a trolling valve V2, and is supplied to the forward hydraulic clutch 3 or the reverse hydraulic clutch 4. Pressure oil from the hydraulic oil pump P is branched in six directions. That is, the operating hydraulic pressure adjusting valve L
1 through the lubricating oil cooler 29, the path from the lubricating oil pressure adjusting valve L2 to the drain circuit, the path of the governor valve V5, and directly to the throttle holes 7.7 of the forward / reverse switching valve V1 without passing through the trolling valve V2. Then, a path leading to the back chamber spool 5 of the operating hydraulic pressure regulating valve L1, a path leading from the trolling valve V2 to the forward / reverse switching valve V1, a path of the operating hydraulic pressure regulating valve L1, and a back chamber 31 of the forward / backward switching valve V1. There are five routes. Reference numeral 18 is a muffling valve.

Then, pressure oil is supplied from the trolling valve V2 to the forward hydraulic clutch 3 or the reverse hydraulic clutch 4 via the forward / reverse switching valve V1, and the operating hydraulic pressure of the forward hydraulic clutch 3 and the reverse hydraulic clutch 4 is determined. This is the operation hydraulic pressure adjustment valve L1 which constitutes a main part of the present invention. Further, the pressure of the operating hydraulic pressure adjusting valve L1 is adjusted by the back chamber spool 5.
And the relief spring 6. The throttle hole 7 of the forward / reverse switching valve V1 is provided in the back chamber portion of the back chamber spool 5 from the hydraulic oil pump P.
・ Pressure oil that has passed through 7 is supplied, and the relief spring 6
The pressure of the operating hydraulic pressure adjusting valve L1 is set so as to gradually increase the relief pressure by pressing the back chamber spool 5.

Further, in the present invention, the back room spool 5
Is also communicated with an oil passage 30 opened and closed by the trolling lever spool 8 of the trolling valve V2. When the trolling lever spool 1 is operated by the trolling lever 1 to the fully engaged side of the hydraulic clutch, the hydraulic oil of the hydraulic oil pump P is supplied to the trolling valve V2.
Through the forward / backward switching valve V1, and is supplied to the forward hydraulic clutch 3 or the reverse hydraulic clutch 4 at a stretch to perform impact fitting. This state is shown in FIG. 7 which shows a conventional impact fitting state.

In FIG. 7, the solid line shows the case where the trolling lever 1 is suddenly operated, and the dotted line shows the case where the trolling lever 1 is slowly operated. When the operator slowly operates the trolling lever 1,
Since the pressure rises slowly over time, the clutch is engaged without impact. However, when a sudden operation is performed as usual, the hydraulic pressure suddenly rises as shown by the solid line in FIG.

In this way, the present invention is configured such that even when the operator performs an abrupt operation, the clutch can be engaged without impact as shown in FIG. 6, that is, in FIG. Is that the hydraulic pressure rises slowly even when the operation is suddenly performed as indicated by the solid line or when the operation is performed slowly as indicated by the dotted line, and no impact occurs when the clutch is engaged.

FIGS. 2, 3, and 4 show a configuration that achieves the above-described operation.
Will be described. In FIG. 2, a trolling lever spool 8 is disposed on the right side, and a trolling spool 24 is disposed on the left side. By the turning operation of the trolling lever 1, the turning pin 22 inserted into the operation shaft 21 turns to rotate the trolling lever spool 8. The trolling lever spool 8 is provided with a groove 8a on the outer circumference, the position of which differs depending on the rotation direction, so that the trolling lever spool 8 rotates when the trolling lever 1 is rotated because the groove 8a is balanced with the position of the drain port 8b. Slide left and right.

[0016] The by transverse sliding of the trolling lever spool 8, changes the biasing pressure of the biasing spring 23 for pressing the trolling spool 24, the trolling spool 24
Is supplied with return oil from the governor valve V5, the position of the trolling spool 24 is determined by the return oil pressure from the governor valve V5 and the urging pressure of the urging spring 23. The ratio of the amount of pressure oil supplied from P to the pump port 25 to the forward / reverse switching valve V1 or the amount of pressure oil ejected to the drain port D is changed. Thereby, trolling pressure adjustment is performed.

According to the first aspect of the present invention, FIG.
As shown in FIG. 5, the back chamber 31 of the trolling lever spool 8 is connected to the drain communication oil passage at a position of approximately 90 degrees while the trolling lever 1 is rotated from the lowest trolling speed position to the fully engaged position by the 105-degree rotation. A drill hole S communicating with d was provided. As shown in FIG. 4, the drill hole S does not communicate with the trolling lever 1 and the trolling lever spool 8 in most cases during the rotation of 105 degrees. It is configured to communicate only at the front position. This allows the operator to set the trolling lever 1
Is operated to the completely fitted position, the drill hole S and the drain communication oil passage d always communicate with each other.
The back spool 1 is retracted to the lowest pressure position, delaying the subsequent rise of the pressure oil.

Next, a second embodiment and a third embodiment will be described. FIG. 8 is a control circuit diagram of a hydraulic control mechanism of a marine deceleration reverser using an electromagnetic valve, FIG. 9 is a drawing showing the relationship between the position of the trolling lever 1 and control, and FIG. 10 is a diagram showing the relationship between the position of the trolling dial 11 and control. Illustrated drawing, FIG.
Is a hydraulic circuit diagram of a hydraulic control mechanism of the marine deceleration reversing machine with the solenoid valve V3 interposed therebetween, FIG. 12 is a control flowchart of FIG. 11, and FIG. 13 is a marine deceleration reversal with the electric pressure reducing valve or the proportional solenoid valve V4 interposed. Circuit diagram of hydraulic control mechanism of machine, FIG. 14
13 is a control flowchart of FIG. 13, and FIG. 15 is a front sectional view of the electric pressure reducing valve or the proportional solenoid valve V4.

FIG. 8 shows the overall configuration of a marine deceleration reversing machine using the solenoid valve V3 or an electric pressure reducing valve or a proportional solenoid valve V4.
-It will be described with reference to FIGS. The rotation of the crankshaft of the engine E is input to the marine deceleration / reversing machine M to disconnect and connect the internal forward hydraulic clutch 3 and reverse hydraulic clutch 4.
Then, an engine speed sensor 44 is provided to the controller C.
And a signal from the output shaft speed sensor 43 are input.
A forward / reverse switching valve V1 is provided to be attached to the marine deceleration reversing machine M, and a forward / backward switching lever 2 for operating the forward / backward switching valve V1 is provided. The trolling valve V2 is interposed between the hydraulic oil pump P and the forward / reverse switching valve V1 as a low-speed valve. An interface, a ROM, a RAM, a CPU, and the like are arranged inside the controller C. 45 and 46 are hydraulic clutch engagement sensors. A trolling state or a completely fitted signal is transmitted from the fully fitted switch 38 to the controller C by the trolling lever 1 or the forward / reverse switching lever 2 shown in FIG. 9 or FIG.

The trolling lever 1 shown in FIGS. 9 and 11
And the trolling dial 11 has a different operation angle, but the trolling control covers about 75% of the range.
The remaining 25% is the fully inserted zone. In FIG. 11, the point that the forward / reverse switching valve V1 and the trolling valve V2 are provided is exactly the same as the hydraulic circuit of FIG. 1, and the operating hydraulic pressure adjusting valve L1 is provided through the throttle hole 7.7 of the forward / backward switching valve V1. The solenoid valve V3 is interposed in a circuit for supplying pressure oil for control to the back chamber spool 5 of the vehicle. Then, during a moment before the trolling lever 1 is changed from the trolling position to the completely fitted position, the solenoid valve V3 is opened to the drain circuit in order to reduce the pressure of the back spool 5 to zero. It is. The time during which the solenoid valve V3 is opened is determined by a timer T as shown in the flowchart of FIG.

FIGS. 13 and 14 show a third embodiment of the present invention. In this embodiment, the trolling valve V2 and the operating oil pressure adjusting valve L1 are not interposed, and an electric pressure reducing valve or a proportional solenoid valve V4 is used instead. The structure of the electric pressure reducing valve or the proportional solenoid valve V4 is shown in FIG.
5 is disclosed. The same applies to the case of using the electric pressure reducing valve or the proportional solenoid valve V4. When the operation of the trolling lever 1 or the trolling dial 11 is determined by the controller C and the operation is completely performed at once, the electric pressure reducing valve or the proportional The operating oil pressure is kept low by the solenoid valve V4. The time is determined by the timer T. In the case of the embodiment of FIG.
Also in the case of this embodiment, the point that the flowchart is operated in order to make the conventional hydraulic pressure rise curve of FIG. 7 into the hydraulic pressure rise curve of FIG. 6 is the same.

[0022]

As described above, the present invention has the following advantages. That is, since the trolling lever 1 and the trolling dial 11 are suddenly operated from the trolling position to the fully engaged position, the back of the operating hydraulic pressure adjusting valve L1 is at a position just before the trolling lever 1 and the trolling dial 11 are completely engaged. Since the pressure in the back chamber of the chamber spool 5 is reduced to zero, the rise of the pressure oil to the hydraulic clutch does not rise sharply, and the forward hydraulic clutch 3 and the reverse hydraulic clutch 4 are not shockably fitted. .

With the structure as claimed in claim 2, the solenoid valve V3
And the timer T are provided in the circuit in the back chamber of the operating hydraulic pressure adjusting valve L1 to prevent the hydraulic clutch from being completely impacted by a simple configuration despite the sudden operation of the complete engagement of the trolling lever 1. Was completed.

Since the electric pressure reducing valve or the proportional solenoid valve V4 is provided in place of the trolling valve V2 and the operating oil pressure adjusting valve L1, the trolling lever 1 can be completely fitted with a simple structure. Despite the sudden operation of the hydraulic clutch, it was possible to prevent the hydraulic clutch from being completely impacted completely.

[Brief description of the drawings]

FIG. 1 is a circuit diagram showing a hydraulic control mechanism according to the first embodiment of the present invention.

FIG. 2 is a front sectional view of the trolling valve V2 according to the first embodiment of the present invention.

FIG. 3 is a side view of the trolling valve V2.

FIG. 4 is a side view showing an operation state of a trolling lever spool 8 of the trolling valve V2.

FIG. 5 is a front cross-sectional view of the operating hydraulic pressure adjustment valve L1.

FIG. 6 is a hydraulic pressure rise curve diagram according to the first embodiment of the present invention.

FIG. 7 is a hydraulic pressure rise curve in a hydraulic control mechanism of a conventional marine deceleration reverser.

FIG. 8 is a control circuit diagram of a hydraulic control mechanism of a marine reduction / reversal device using an electromagnetic valve.

FIG. 9 is a diagram showing the relationship between the position of the trolling lever 1 and control.

FIG. 10 is a diagram showing the relationship between the position of a trolling dial 11 and control.

FIG. 11 is a hydraulic circuit diagram of a hydraulic control mechanism of the marine deceleration reverser equipped with an electromagnetic valve V3.

FIG. 12 is a flowchart of the control in FIG. 11;

FIG. 13 is a hydraulic circuit diagram of a hydraulic control mechanism of the marine deceleration reverser equipped with an electric pressure reducing valve or a proportional solenoid valve V4.

FIG. 14 is a flowchart of the control in FIG. 13;

FIG. 15 is a front sectional view of an electric pressure reducing valve or a proportional solenoid valve V4.

[Explanation of symbols]

 V1 Forward / reverse switching valve V2 Trolling valve V3 Solenoid valve V4 Electric pressure reducing valve or proportional solenoid valve V5 Governor valve L1 Operating oil pressure adjusting valve L2 Lubricating oil pressure adjusting valve S drill hole T Timer 1 Trolling lever 2 Forward / reverse switching lever 3 Forward hydraulic clutch Reference Signs List 4 reverse hydraulic clutch 5 back chamber spool 6 relief spring 7 throttle hole 8 trolling lever spool 11 trolling dial

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16H 61/00-61/24 B63H 23/30

Claims (3)

(57) [Claims] 1. A hydraulic circuit for a marine deceleration / reversing machine, comprising a hydraulic oil pump P, a trolling valve V2, a forward / reverse switching valve V1, and a forward / reverse clutch 3, 4; in a state that takes into forward or backward switching valve V1, when switched suddenly completely fitted position trolling valve V2 from trolling position, once in order to lower pressure hold hydraulic fluid pressure to be pressure regulated in work dynamic hydraulic pressure regulation valve L1 Of the back chamber spool 5 for adjusting the pressure of the operating oil pressure adjusting valve L1
The back chamber is connected to the trolling valve V2 body by piping,
The trolling valve V2 is connected to the back chamber of the back chamber spool 5.
Trolling lever that opens and closes the oil passage 30 for pressurized oil
The trolling lever spool 8
Of the trolling lever 1 for manually operating the trolling lever 1 at a certain angle
From the lowest trolling position to the fully engaged position
Trolling lever spool 8 on the way during operation
Then, the back room 31 of the trolling lever spool 8 is drained.
A drill hole S communicating with the communication oil passage d is provided.
Means trolling lever 1 and trolling lever spoo
During the rotation of the screw 8 by a certain angle, the door
The lane communication oil passage d and the back room 31 are configured to communicate with each other.
The lator operates the trolling lever 1 to the fully engaged position
The drill hole S and the drain communication oil passage d
The back spool 5 of the hydraulic pressure adjusting valve L1 communicates with the minimum pressure.
And the pressure oil rises afterwards.
A hydraulic control mechanism for a marine deceleration reversing machine, characterized in that it is configured to delay rebound. 2. A hydraulic circuit of the marine reverse and reduction gear, the hydraulic circuit, in those with hydraulic oil pump P · trolling valve V2, the forward-reverse switching valve V1, the forward-reverse clutch 3, 4, trolling valve Operates directly without going through V2
Circuit of forward / reverse switching valve V1 from oil pump P and throttle hole 7.7
And the forward / reverse switching valve V1 is moved forward or backward.
In the state, the trolling valve V2 is moved to the trolling position.
Hydraulic pressure adjustment when suddenly switching from
The hydraulic oil pressure regulated by the valve L1 is temporarily maintained at a low pressure.
In order to achieve this, the hydraulic oil is passed through the throttle holes 7.7 of the forward / reverse switching valve V1.
Supply pressure oil for control to the back chamber spool 5 of the pressure regulating valve L1
A solenoid valve V3 is interposed in the circuit of
The back chamber of the back chamber spool 5 for adjusting the pressure of
V3, and the other of the solenoid valves V3 communicates with the drain circuit D.
Trolley that constitutes a trolling valve V2
Trolling lever for manually operating the lever 8
-1 and the solenoid valve V3 are linked, and the trolling valve V2 is
For a moment before changing from the trolling position to the fully engaged position
In order to make the pressure of the part of the back room spool 5 zero
The solenoid valve V3 is configured to open to the drain circuit,
The opening time of the valve V3 is determined by the timer T.
Hydraulic control mechanism for marine speed reducer. 3. A hydraulic circuit for a marine deceleration reversing machine, comprising: a hydraulic oil pump P;
Pneumatic pressure reducing valve or proportional solenoid valve V4, forward / backward switching valve V1, front
In the hydraulic control mechanism provided with the reverse clutches 3 and 4,
Rolling lever 1 or trolling dial 11
The operation is judged by the controller C, and the forward / backward switching valve
When V1 is fully engaged at a stretch, the operating oil pressure is lowered.
The electric pressure reducing valve or the proportional solenoid valve V4
Interposed between pump P and forward / reverse switching valve V1 to switch between forward and backward
When the valve V1 is operated forward or backward, the electric
The energizing time of the pressure reducing valve or the proportional solenoid valve V4 is determined by the timer T.
Control, the pressure is regulated by the hydraulic pressure control valve L1.
A hydraulic control mechanism for a marine deceleration reversing machine, wherein the hydraulic oil pressure is temporarily maintained at a low pressure .