JPH0245535Y2 - - Google Patents

Description

[Detailed Description of the Invention] This invention relates to a marine propulsion device equipped with a hydraulic clutch.

This type of marine propulsion system is used, for example, when trying to hold a firefighting boat in a fixed position against the tide, when making a fish boat sail at low speed following a school of swimming fish, when bringing a tugboat to shore, etc. As is well known in the art, this objective is achieved by reducing the hydraulic pressure applied to the above-mentioned hydraulic clutch below the normal hydraulic pressure set by the primary pressure regulating valve and operating the clutch in slip mode. Conventionally, to reduce the clutch operating hydraulic pressure in this way, a pressure reducing valve, generally called a low speed valve, is inserted and installed in the oil supply circuit for the hydraulic clutch, and the pressure is obtained by the action of the pressure reducing valve. The drain oil from the valve is
It is used as a lubricating oil together with the relief oil from the primary pressure regulating valve, and the oil pressure of such lubricating oil is set by the secondary pressure regulating valve.

When obtaining clutch slip operation by reducing the clutch working oil pressure with a pressure reducing valve as described above, it is recommended to change the degree of pressure reduction over a wide range and change the clutch slip rate over a wide range. Since it is impossible to control the spring load of the valve spring over a wide range because it is impossible due to the structure of the pressure reducing valve, it is impossible to control the spring load of the valve spring. The clutch operating oil pressure cannot be reduced below the set pressure of the secondary pressure regulating valve that sets the lubrication oil pressure, and for these two reasons, the clutch slip ratio that can be obtained is limited to a relatively narrow range. . Furthermore, it is of course difficult to stably obtain a desired clutch slip ratio in a system in which the clutch slip ratio is increased or decreased by manually operating a pressure reducing valve.

One purpose of this invention is to create a new marine propulsion system equipped with a hydraulic clutch that can stably obtain clutch slip ratios over a wide range, in contrast to the conventional systems described above. , to provide.

As one means to achieve this purpose, this invention uses an electromagnetic flow regulating valve as described later, but another purpose of this invention is that the electromagnetic flow regulating valve operates electrically. To provide a new marine propulsion device which uses a clutch slip operation mechanism to take measures against electrical system failures.

This invention will be described in detail below with reference to the illustrated embodiments.

In FIG. 1 showing the first embodiment, 1 is a clutch portion of a marine propulsion device, and 2 is an output shaft of the clutch portion 1. In FIG. The illustrated embodiment is an example in which this invention is implemented in a vessel such as a tugboat, in which forward and backward switching of the vessel is performed by changing the direction of the propeller by rotational displacement of the end portion of the propulsion device including the propeller. Correspondingly, the clutch part 1 includes only one multi-plate hydraulic clutch 3, that is, a friction element 3a on the driving side and a friction element 3 on the driven side.
A multi-disc hydraulic clutch 3 is provided, which is configured to obtain clutch engagement by frictionally engaging the piston 3c with the piston 3b by advancing the piston 3c against the force of the return spring 3d by hydraulic action. . The output shaft 2 is interlocked and connected to a propeller shaft (not shown) as usual.

Similarly, as shown in FIG. 1, a discharge circuit 7 end of a hydraulic pump 6 that sucks and discharges hydraulic oil from an oil tank 4 via a suction filter 5 controls the supply and discharge of hydraulic oil to and from a hydraulic clutch 3. switching valve 8
This switching valve 8 has two positions: an operating position I that supplies hydraulic oil to the hydraulic clutch 3, and a neutral position that discharges hydraulic oil from the hydraulic clutch 3 and returns it to the oil tank 4 via an oil drain circuit 9. It consists of a two-position valve with N. A drain circuit 10 connected to the discharge circuit 7 includes a primary pressure regulating valve 11 for setting the normal operating oil pressure for the hydraulic clutch 3 and a secondary pressure regulating valve 12 for setting the lubricating oil pressure.
are inserted and installed in this order, and both pressure regulating valves 1
1 and 12, a lubricating oil supply circuit 13 supplies lubricating oil from the drain circuit 10 to the friction elements 3a, 3b of the hydraulic clutch 3, the bearing portion of the clutch portion 1, and other lubricated portions L. is derived. Another drain circuit 14 connected to the discharge circuit 7 is provided with an overload relief valve 15 that has a higher relief pressure than the primary pressure regulating valve 11 .

The circuits connecting the switching valve 8 and the hydraulic clutch 3, except for the common circuit 16 located on the switching valve 8 side and the common circuit 17 located on the hydraulic clutch 3 side, are connected in particular to the first connections connected in parallel to each other. Circuit 18 and the second
It is also configured with a connection circuit 19. The following mechanism is provided to reduce the hydraulic pressure set by the primary pressure regulating valve 11 and apply it to the hydraulic clutch 3 to cause the clutch 3 to operate in slip mode.

That is, the mechanism includes an electromagnetic flow regulating valve 22 inserted into the first connecting circuit 18 and a drain circuit 23 connected to the first connecting circuit 18 on the side of the hydraulic clutch 3 from the electromagnetic flow regulating valve 22. It also includes a diaphragm 24 inserted therein.
A solenoid valve 25 is also inserted into the drain circuit 23 described above, and this solenoid valve 25 has a conduction position A that keeps the drain circuit 23 in a conductive state and a cutoff position B that shuts off the drain circuit 23. has been done.

An electric controller 26 is provided to control the flow rate throttled by the electromagnetic flow control valve 22. This electric controller 26 controls a command value Sp corresponding to the throttle flow rate set to the electromagnetic flow rate adjustment valve 22.
can be set, and the output rotational speed Sr of the hydraulic clutch 3 can be input as another control signal. That is, a toothed wheel 27 is fixedly installed on the output shaft 2, and this toothed wheel 2
A magnetic pick-up 28 is provided oppositely to the tooth ring 27 and the magnetic pick-up 28.
A rotation speed detector 29 is constituted by the rotation speed detector 29, and an output signal of the rotation speed detector 29 for detecting the rotation speed of the output shaft 2 is inputted to the electric controller 26 as the output rotation speed Sr. The above-mentioned instruction value Sp is designed to be set as a converted value corresponding to the output rotation speed of the hydraulic clutch 3. Then, the electric controller 26 controls the set instruction value Sp.
Control signal according to input output rotation speed Sr
Sc, and the electromagnetic flow rate is adjusted so that the clutch output rotation speed corresponding to the indicated value Sp is obtained, that is, the difference between the rotation speed corresponding to the indicated value Sp and the actual clutch output rotation speed Sr becomes zero. The control valve 22 or its variable throttle controls the flow rate. The electric controller 26 also outputs a slip operation command signal Sca to control the solenoid 25a of the electromagnetic valve 25 when a value corresponding to the output rotation speed obtained by slip operation of the hydraulic clutch 3 is set as the instruction value Sp.
energizes the spring 2 in the direction of the cutoff position B.
The electromagnetic valve 25, which is biased at 5b, is moved to the conducting position A.

The above-mentioned electromagnetic valve 25 is connected to the drain circuit 2.
In addition to 3, the electromagnetic valve 25 is also inserted into the second connection circuit 19, and the electromagnetic valve 25 interrupts the second connection circuit 19 at the conducting position A, and closes the second connection circuit 19 at the cutoff position B. It is configured as a valve that brings the connection circuit 19 into a conductive state.

In order to protect the electromagnetic flow rate regulating valve 22, a line filter 31 made of fine paper with a diameter of, for example, 10 microns is inserted into the oil supply circuit 18 on the primary side of the regulating valve 22. It has been attached as a related matter. In addition, the primary pressure regulating valve 11
is constructed of a hydraulic pressure gradually increasing type known from Japanese Utility Model Publication No. 57-3048, etc., and the common circuit 16 is located behind the control piston that receives the end of the valve spring.
When the switching valve 8 is moved from the neutral position N to the working position I, a throttle 32 is used to gradually apply hydraulic pressure to gradually increase the valve spring load, and when the switching valve 8 is moved from the working position to the neutral position N. The piston is connected via a check valve 33 for quickly draining oil from behind the control piston and quickly retracting the piston when the piston is turned off.

In FIG. 1, 34 is a line filter inserted into the discharge circuit 7, and 35 and 36 are a line filter and an oil cooler inserted into the lubricating oil supply circuit 13, respectively.

Next, the operation of the first embodiment shown in FIG. 1 will be explained. With the switching valve 8 moved to the operating position I as shown in FIG. 1, the operation of the hydraulic clutch 3 is as follows. It will be held in That is, first, when setting the instruction value Sp of the value corresponding to the output rotation speed obtained when the hydraulic clutch 3 is operated in a non-slip operation state to the electric controller 26, a control signal Sc of a corresponding value is output. The degree of restriction of the electromagnetic flow control valve 22 is minimized, and
The slip operation command signal Sca is not output, and the electromagnetic valve 25 is placed in the cutoff position B, which cuts off the drain circuit 23 and makes the second connection circuit 19 conductive. Therefore, the hydraulic oil flows from the secondary side of the switching valve 8 through the first and second connection circuits 18 and 19 to the hydraulic clutch 3 without being substantially throttled by the electromagnetic flow control valve 22, and without being substantially throttled by the drain circuit. 2
The hydraulic pressure applied to the hydraulic clutch 3 at that time becomes the normal hydraulic pressure set by the primary pressure regulating valve 11, and the hydraulic clutch 3 is operated in a non-slip state. Ru.

Next, when setting a command value Sp to the electric controller 26 such that an arbitrary output rotation speed can be obtained by slip operation of the hydraulic clutch 3,
The throttle degree or throttle flow rate of the electromagnetic flow regulating valve 22 is set to an appropriate value by outputting the corresponding control signal Sc, and the slip operation command signal Sca is output, causing the electromagnetic valve 25 to make the drain circuit 23 conductive. The second connection circuit 19 is then moved to the conducting position A where it is cut off. Therefore, the hydraulic pump 6
The discharged oil is supplied to the hydraulic clutch 3 only through the first connection circuit 18, and the flow rate of the discharged oil is throttled by the electromagnetic flow rate regulating valve 22, so that the oil flow rate to the secondary side of the regulating valve 22 is reduced. circuit 18 on the secondary side of such an electromagnetic flow regulating valve 22.
From then on, oil is constantly drained at a rate determined by the throttle 24 in the drain circuit 23. In this way, the electromagnetic flow rate adjustment valve 22 is controlled by the flow rate control by the electromagnetic flow rate adjustment valve 22 and the oil drain through the throttle 24.
Since the hydraulic pressure in the first connecting circuit 18 on the secondary side can be reduced to an arbitrary value lower than the normal hydraulic pressure set by the primary pressure regulating valve 11, the hydraulic clutch 3 resists the force of the return spring 3d. By maintaining the forward position of the piston 3c at an arbitrary position, the hydraulic clutch 3 can be operated at an arbitrary slip rate. That is, since the low oil pressure for slip-operating the hydraulic clutch 3 can be obtained by flow control without reducing the oil pressure on the primary side of the electromagnetic flow regulating valve 22, the low oil pressure can be obtained by controlling the secondary pressure regulating valve 12 for setting the lubrication oil pressure as the low oil pressure. Even when obtaining a hydraulic pressure lower than the set hydraulic pressure, both the primary pressure regulating valve 11 and the secondary pressure regulating valve 12 continue the relief operation, and lubricating oil of the desired lubricating pressure is supplied to the lubricated part L. . During the slip operation of the hydraulic clutch 3, the electric controller 26 receives the actual clutch output rotation speed Sr as described above and adjusts the electromagnetic flow rate so that the difference between the command value Sp and the output rotation speed Sr becomes zero. Since the control signal Sc that controls the throttle flow rate by the valve 22 is output, the slip rate or output rotation speed of the hydraulic clutch 3 is automatically and stably maintained at a value corresponding to the command value Sp by feedback control. It is controlled to be constant. It is also possible to freely change the navigation speed by changing the instruction value Sp while the ship is navigating.

Next, when the electrical system malfunctions for some reason, the electrical controller 26 will no longer operate, and the electromagnetic flow regulating valve 22 will essentially be connected to the first connection circuit 18.
At the same time, when the slip operation command signal _Sca disappears, the electromagnetic valve 25 is moved to the cutoff position B by the force of the spring 25b, and the drain circuit 23 is cut off. However, at this time, the second connection circuit 19 is brought into conduction by the electromagnetic valve 25, so that the hydraulic oil can be supplied and discharged from the hydraulic clutch 3 by the second connection circuit 19. That is, the switching valve 8 is moved to the operating position I, and hydraulic oil at the normal oil pressure set by the primary pressure regulating valve 11 is supplied to the hydraulic clutch 3 via the circuit 19, and the switching valve 8 is moved to the neutral position N. The same circuit 1
Oil can be drained from the hydraulic clutch 3 via 9 to sail and stop the ship. Therefore, even if the electrical system fails, the ship can safely return to port.

Next, a second embodiment shown in FIG. 2 will be described. In this second embodiment, a third connection circuit 40 is provided in parallel to the second connection circuit 19, and a third connection circuit 40 is provided in parallel to the second connection circuit 19. A check valve 41 that allows oil to flow only in the direction of the hydraulic clutch 3 is inserted into the circuit 18, and a check valve 42 that allows oil to flow only in the direction of the switching valve 8 is inserted in the third connection circuit 40. It is installed. Then, a pump port and a clutch port for each one are added to the solenoid valve 25, and the third connection circuit 40 is passed through the solenoid valve 25, and the solenoid valve 25 is connected to the same drain circuit 23 as described above. The third connection circuit 40 is made conductive at the conduction position A, and the valve is configured to shut off the third connection circuit 40 at the cutoff position B of the drain circuit 23 similar to the above. The construction of other parts in the second embodiment is made equal to the construction of the corresponding parts in the embodiment shown in FIG.

Since the second embodiment shown in FIG. 2 is configured as described above, the slip operation command signal Sca
When the solenoid valve 25 is moved to the conducting position A by the output of As a result, the hydraulic oil is blocked in the oil supply direction and is supplied in the direction of the hydraulic clutch 3 through the first connection circuit 18 as in the first embodiment, but the switching valve 8 is moved from the slip operation state to the neutral position. When shifting to N and attempting to stop the operation of the hydraulic clutch 3, the first connection circuit 18 is blocked by the check valve 41 in the oil draining direction. This is done through the connection circuit 40 of No. 3.

In this way, the oil from the hydraulic clutch 3 is drained through the third connection circuit 40 without passing through the first connection circuit 18 in which the electromagnetic flow control valve 22 and the very fine line filter 31 are inserted. By doing so, the oil from the hydraulic clutch 3 can be drained quickly without being restricted by the electromagnetic flow rate regulating valve 22 or its variable throttle and line filter 31, and the desired clutch operation can be stopped quickly. It will be done. Furthermore, the line filter 31, which is made of extremely fine paper, has the property of being strong against oil flow in the forward direction but weak against oil flow in the opposite direction. On the other hand, by eliminating the oil flow in the opposite direction as described above, the line filter 31 is protected and its life span is improved.

Other functions of the second embodiment are similar to those described for the first embodiment.

As is clear from the above description, in the marine propulsion system of this invention, in the marine propulsion system equipped with the hydraulic clutch 3, there is a connection between the switching valve 8, which controls the supply and discharge of hydraulic oil to and from the hydraulic clutch 3, and the hydraulic clutch 3.
A first connection circuit 18 and a second connection circuit 19 are provided in parallel with each other, and a mechanism for reducing the hydraulic pressure applied to the hydraulic clutch 3 to operate the clutch 3 in slip mode is provided in the first connection circuit 18. Consisting of an electromagnetic flow rate adjustment valve 22 inserted therein and a throttle 24 inserted in a drain circuit 23 connected to the first connection circuit 18 on the side of the hydraulic clutch 3 from the electromagnetic flow rate adjustment valve 22. At the same time, an electric controller 26 is set with a command value Sp and receives the clutch output rotation speed Sr, and controls the flow rate throttled by the electromagnetic flow rate adjustment valve 22 so as to obtain a clutch slip rate according to the command value Sp. and an electromagnetic valve 25 that selectively conducts and shuts off the drain circuit 23, which resists the force of the spring 25b and moves to the conduction position A of the drain circuit 23 in response to the slip operation command signal Sca from the electric controller 26. A solenoid valve 25 that can be displaced is provided, and the solenoid valve 25
is configured as a valve that shuts off the second connection circuit 19 at the conduction position A of the drain circuit 23 and brings the second connection circuit 19 into the conduction state at the disconnection position B of the drain circuit 23. And,
It has the following advantages:

That is, in the marine propulsion system of this invention, the mechanism for slip-operating the hydraulic clutch 3 is not a pressure reducing valve as in the conventional case, but the electromagnetic flow rate adjusting valve 22 and the throttle 24 in the drain circuit 23 as described above.
The oil flow rate of the first connection circuit 18 on the secondary side of the regulating valve 22 is limited by the electromagnetic flow regulating valve 22, and the secondary side of such electromagnetic flow regulating valve 22 In combination with constant draining of oil through the throttle 23, the hydraulic pressure applied to the clutch 3 can be reduced by restricting the supply of hydraulic oil to the hydraulic clutch 3. The flow rate can be controlled over a wide range by the variable throttle of the former and the fixed throttle 24 in the drain circuit 23, and the pressure can be reduced by restricting the flow rate of the oil supply circuit 18 on the secondary side of the electromagnetic flow regulating valve 22. Therefore, the oil pressure on the primary side of the regulating valve 22 is not lowered, and the clutch working oil pressure can be reduced to a value lower than the setting pressure of the secondary pressure regulating valve for setting the lubricating oil pressure.
The hydraulic clutch can be operated in slip mode over a wide range of slip rates from approximately 0% to 100%, greatly expanding the range of changes in sailing speed by clutch slipping. Further, in the marine propulsion system of this invention, the throttle flow rate by the electromagnetic flow rate adjustment valve 22 is controlled by the electric controller 26 as described above, using feedback control using the clutch output signal as a feedback signal. Compared to conventional systems in which the clutch slip rate was controlled only by manually adjusting the degree of pressure reduction by the pressure reducing valve, the desired clutch slip rate can be obtained stably.

Furthermore, in the marine propulsion system of this invention, an electromagnetic flow regulating valve 22 is inserted between the switching valve 8 and the hydraulic clutch 3 for causing the hydraulic clutch 3 to operate in slip mode, and oil is drained through the throttle 24 during slip operation. In addition to the first connection circuit 18, a second connection circuit 19 is provided in parallel with the circuit 18 to receive a slip operation command signal from the electric controller 26.
The second connection circuit 19 is automatically brought into conduction by the electromagnetic valve 25 which makes the drain circuit 23 conductive by Sca and enables the slip operation of the hydraulic clutch 3 when the slip operation command signal Sca is not output. If the electrical system fails and slips, the operation command signal Sca
When the output stops, the second connection circuit 19 is automatically brought into conduction, and hydraulic oil can be freely supplied and discharged from the hydraulic clutch 3 through the second connection circuit 19. Therefore, a mechanism for clutch slip operation is skillfully provided to enable automatic operation of the hydraulic clutch in the event of an electrical system failure.

[Brief explanation of the drawing]

Figures 1 and 2 are the first part of this invention.
FIG. 2 is a hydraulic circuit diagram and block diagram showing an embodiment of the present invention and a second embodiment. DESCRIPTION OF SYMBOLS 1...Clutch part, 2...Output shaft, 3...Hydraulic clutch, 6...Hydraulic pump, 8...Switching valve, 1
1... Primary pressure regulating valve, 18... First connection circuit, 1
9... Second connection circuit, 22... Solenoid flow rate adjustment valve, 23... Drain circuit, 24... Throttle, 25...
...Solenoid valve, 25a...Solenoid, 25b...
... Spring, 26 ... Electric controller, 29
...Rotation speed detector, 40...Third connection circuit, 4
1,42...Check valve, Sp...Indication value, Sr...Output rotation speed, Sc...Control signal, Sca...Slip operation command signal.

Claims (1)

[Scope of utility model registration request] In a marine propulsion system equipped with a hydraulic clutch,
A first connection circuit and a second connection circuit are provided in parallel with each other between the switching valve that controls the supply and discharge of hydraulic oil to and from the hydraulic clutch and the hydraulic clutch, and the hydraulic pressure applied to the hydraulic clutch is reduced to operate the clutch. A mechanism for slip operation is inserted into the electromagnetic flow rate adjustment valve inserted into the first connection circuit and a drain circuit connected to the first connection circuit on the hydraulic clutch side from the electromagnetic flow rate adjustment valve. The controller is configured with an installed throttle, and when an instruction value is set and the clutch output rotation speed is input, the throttle flow rate by the electromagnetic flow rate adjustment valve is controlled so as to obtain a clutch slip rate according to the instruction value. and an electromagnetic valve for selectively conducting and cutting off the drain circuit, the electromagnetic valve being displaced to the conducting position of the drain circuit against a spring force by a slip operation command signal from the electric controller. A valve is provided, and the electromagnetic valve is configured to be a valve that shuts off the second connection circuit when the drain circuit is in a conducting position, and brings the second connection circuit into a conductive state when the drain circuit is in a cutoff position. A marine propulsion system.