JPS5933756Y2 - Hydraulic device for hydraulically tiltable boat propeller drive unit - Google Patents

Description

[Detailed Description of the Invention] The present invention is a hydraulic device for controlling the trimming and tilting motion of a hydraulic tilting propeller drive unit for boats, which fixes a part of the tiltable propeller drive unit to a boat. The present invention relates to a hydraulic device comprising a reversible pump arranged to deliver pressure medium from a tank to a double-acting piston-cylinder device connected to a section.

Propeller drive unit that can be tilted when the boat is stationary and trimmed when the boat is moving, i.e. varying the angle of the unit relative to the boat to optimize the use of engine power The propeller drive unit is designed to allow
The slope has two main requirements during movement.

In the former case, i.e. when the boat is stationary and the drive unit is tipped, so that the drive unit receives no forward thrust, the drive unit must be able to swing over a wide angle relatively quickly. However, such a movement is relatively easy to perform since the force required for it is relatively small.

In the latter case, i.e. when trimming the drive unit while the boat is in motion and as a result the drive unit receives a strong forward thrust thrust, compared to tilting the drive unit as the propulsive forces have to be overcome at the same time Requires a lot of force.

However, when trimming the drive unit, a relatively small tilt only requires a movement, which does not need to be done quickly.

As is known, for example, from Swedish patent no. This can be achieved by providing one hydraulic cylinder that acts to tilt the drive unit and another hydraulic cylinder with a large piston area that controls the trimming of the drive unit when the boat is in motion.

In this way, a small force fast ramp motion and a large force slow motion can be provided using a single constant delivery pump.

However, having to use double hydraulic cylinders is disadvantageous both from an economic and structural point of view.

One significant drawback in this regard is that it is very difficult to find enough space to accommodate the second cylinder.

An object of the present invention is to provide a hydraulic device that can perform the two control functions described above with just one hydraulic cylinder.

Therefore, according to the invention, the trimming and tilting of a hydraulic tilting propeller drive unit for a boat is for controlling the movement, the part of the tilting propeller drive unit being connected to a fixed part. A hydraulic device is provided that includes a reversible pump arranged to deliver pressure medium from a tank to a double-acting piston-cylinder device, the hydraulic device connecting a cylinder chamber on the piston rod side to a cylinder chamber on the opposite side. It is characterized by having a valve device that can be adjusted to a first position where the piston rod side cylinder chamber is connected to the tank and a second position where the cylinder chamber on the piston rod side is communicated with the tank.

In the first position of the valve arrangement, which effectively shorts the two cylinder chambers, the pressure medium discharged from the cylinder chamber on the piston rod side is pumped as it is supplied by the pump to the chamber installed on the opposite side of the piston slot. It will pass to the cylinder chamber on the opposite side.

Effective piston area on which the pressure medium from the pump acts,
Therefore, the difference between the piston areas in the two cylinder chambers is equal to the area of the piston rond.

Since this is significantly less than the total piston area, the piston will move with less force than is required to tilt the drive unit rapidly.

Here, a hydraulic cylinder similar to the corresponding cylinder in the aforementioned Swedish Patent No. 220881,
Assume that the arrangement is such that outward movement of the piston rond tilts the propeller drive unit.

In the other position of the valve arrangement, the cylinder chamber on the piston rod side is brought into communication with the tank, and the pressure medium passed through the cylinder chamber on the opposite side acts on the entire piston area, which affects the movement of that piston and This means that a subsequent tilting movement of the drive unit occurs at a slow speed and with the greater forces required during trimming of the unit.

Since it is necessary to overcome the forward acting thrust during trimming of the drive unit, the pump has to generate a considerably higher pressure in the system than when tilting the drive unit.

A preferred embodiment of the invention takes advantage of this pressure differential and includes a pressure actuated device that automatically adjusts the valve device to first and second positions depending on the pressure within the system. It is characterized by the presence of

The pressure actuated device therefore adjusts the valve device to the first position when the load on the piston rond is low and the pressure in the system is relatively low, such as when the boat is stationary, and also provides a predetermined forward action. When the pressure in the system exceeds a predetermined value due to a larger load on the piston rond due to the propulsive force, the valve device is adjusted to the second position.

According to another embodiment of the invention, the valve arrangement includes a manually adjustable valve element for setting it in a first and a second position.

This manually adjustable valve element is preferably combined with a known non-return valve connected to the gear mechanism of the drive unit, which prevents the piston from moving when the boat is switched from forward motion to reverse motion. The pressure medium conduit from the cylinder chamber on the rod side is closed off.

Both of the previously described embodiments allow the tilting of the drive unit to be carried out by means of the drive unit's manual mechanism which is normally provided for movement and trimming, thus requiring no extra manual mechanism which would complicate the operation of the drive unit. does not require.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The hydraulic device of the present invention will be described in more detail below with reference to embodiments illustrated in the accompanying drawings.

The known hydraulic device shown in FIG.
It includes a liquid pump 1 driven by.

The electric motor can be rotated in either direction, so the pump can pump liquid in both left and right directions.

For this purpose, the pump is connected via a check valve 4.5 to a liquid tank 6, which is shown above the two lines 2, 3.

This pump is also connected to the tank 6 by a line 7.8 with an overload valve 9,10.

Depending on the direction of rotation of the electric motor, one of the pipes 2 and 3 becomes a suction pipe and the other a pressure pipe, and the pump is connected to two control valves 1.
Connected to 1 and 12.

The control valve 11 has a conduit 1 connected to one cylinder space 16 of the double-acting hydraulic cylinder 17 and a cylinder space 18 of the single-acting hydraulic cylinder 19 for controlling the supply and discharge of pressure medium.
3.14.

The other control valve 12 is connected to the other cylinder space 20 of the double-acting hydraulic cylinder 17 by a line 15 .

These control valves 11, 12 are also connected to return lines 21, 22 and are provided with actuating pistons 25, 26.

These actuating pistons are adapted to be varied by the pressure in the lines 2 and 3, respectively, against the action of springs 23 and 24, so that the actuating pistons are adapted to be varied by the pressure in the lines 2 and 3, respectively, so that the actuating pistons , 14° and 15 to control communication with the return pipes.

The hydraulic device includes a pipe line 15 communicating with the cylinder space 20.
A manually adjustable shut-off valve 27 disposed within the pipe line 13
, 15.

Pipe line 3 provided in the piston 32 of the double-acting hydraulic cylinder 17
1 is further arranged with an overload valve 30, whose line 31 connects the two cylinder spaces 16.20.

Furthermore, the short-circuit pipe 2 is connected via another overload valve 48.
A conduit 33 is also provided connecting 8 with the tank.

The amount of leakage in this hydraulic device is negligible,
When the pump is not in operation, this hydraulic system is operated by pistons 32. of two hydraulic cylinders 17.19.
34 with their corresponding rods 35, 36 are held in their adjusted position.

The hydraulic cylinders are arranged between the fixed structural elements of the boat, namely the stern transom, and the tilting drive unit, such that outward movement of the respective piston rod 35, 36 causes the drive unit to tilt upwards.

If you change the settings of the drive unit, i.e. tilt the drive unit up or down for trimming, pump 1
The motor is started in the desired direction and is stopped when the desired setting of the drive unit is obtained.

Assuming that the boat is stationary and the drive unit is in the downward operating position and is about to tip upwards, the hydraulic system operates as follows.

The pump motor is started in such a direction that line 3 becomes the suction line and line 2 becomes the pressure line.

The pressure in line 2 opens a spring-loaded check valve 37, which is arranged in control valve 11 and has the form of a ball valve, so that the pressure medium passes through lines 13, 14 into each of the cylinders 17, 18. Sent to space 16°18.

At the same time, the pressure in line 2 actuates the actuating piston 26 in the control valve 12, so that the piston 26 opens the check valve 38 disposed in the control valve 12, opening the line 15 and the return line. The cylinder space 20 of the cylinder 17 and the tank 6 are connected via a channel 22 .

Since the piston area of the piston 32 is smaller than that of the piston 34 and the same pressure is in the cylinder spaces 16 and 18, the piston rod 35 of the piston 32 is rapidly moved outwards, thus forcing the drive unit upwards. Tilt.

When the drive unit is lowered, the direction of rotation of the electric motor is reversed, so that line 3 is on the pressure side,
Pipe line 2 becomes the suction side.

Pressure medium is passed into the cylinder chamber 20 of the cylinder 17 through a spring-loaded check valve 39 arranged in the control valve 12 .

At the same time, the pressure in the line 3 increases to the working piston 2 of the control valve 11.
5 opens the spring-loaded check valve 40, and the cylinder space 16.18 is connected to the tank 6 through the line 13, the check valve 40 and the return line 21.

The drive unit is pulled down by the inward movement of the piston thus obtained.

The boat is moving, which causes piston rod 35
．． 36 are subjected to a force trying to move them inwardly by a forward thrusting motion, cylinder 1T, due to its small piston area, will generate an outward force large enough to overcome this thrust. Also, the drive unit cannot be swung for trimming.

When trimming the drive unit, during which the flow of liquid through the hydraulic device corresponds to the flow pattern described above for tilting the drive unit, the short tilt movement is further enhanced by the larger piston area of the piston 34 of the cylinder 19. done with great force.

In this respect, this cylinder 19 is suitably installed to provide a relatively long line of force application, which means that when trimming the drive unit, the tilt only requires a relatively short oscillation compared to the oscillation required in the movement. It must be stated that the necessary facts make it possible.

On the other hand, the cylinder 17 is arranged so as to provide a relatively short line of force application to provide a rapid and short oscillation of the drive unit.

Of the other valves 27, 29, 30 incorporated in the hydraulic system, valve 27 acts as a check valve and can be manually adjusted in conjunction with the gear mechanism of the drive unit, so that when the boat is in reverse the cylinder Preventing the flow of liquid from space 20.

In this way, the drive unit is not tilted upwards by the backward thrust of the boat.

The valve 29 allows the cylinder space 20 to be evacuated during the forward movement of the bow if the drive unit is subjected to a large backward force, for example when it bottoms out or collides with an underwater obstacle.

Valve 30 performs a similar function when check valve 27 is closed.

A hydraulic device according to the invention will now be described with reference to FIG. 2, all components corresponding to those provided in the device shown in FIG. 1 being provided with the same reference numerals.

The hydraulic system shown in FIG. 2 corresponds to the hydraulic system shown in FIG. 1 with the following exceptions.

That is, the control valve 12 has been replaced with the control valve 41, and the hydraulic cylinder 19 has been removed.

The hydraulic cylinder 17 is of the same construction as the cylinder of the previously mentioned known device, but of larger dimensions.

Similar to control valve 12, control valve 41 has actuating piston 26
, the piston being actuated by the pressure in the line 2 against the action of a spring 42.

A check valve 38 is provided in the line connecting the line 15 to the cylinder space 20 and the return line 22 to the tank 6.

The hydraulic system also includes a check valve 39 installed at the connection of the control valve 41 with the line 3 .

Furthermore, the control valve 41 has another actuating piston 44 biased by a spring 43 and actuated by the pressure in the line 2, which piston 44 is provided at the connection with the line 15. Activate valve 45.

Check valve 46 is arranged in series with valve 45.

When tilting the drive unit upwards, the device of FIG. 2 operates as follows.

Pressure liquid is supplied to line 2, valve 37 of control valve 11 and line 13.
When pumped through the cylinder space 16 , a pressure is created within the hydraulic device, the magnitude of which depends on the counterpressure acting on the piston 32 .

This pressure, which is relatively low when the boat is stationary and no forward acting thrust is transmitted to the piston rod, is transmitted to the chamber 47 of the control valve 41 and the two working pistons 26
．． 44.

The spring force of the two actuating piston springs 42,43 causes the actuating piston 44 to open the valve 45 at this relatively low pressure, while the actuating piston 26 is held in the inoperative position by the spring 42, so that the valve 38 is adjusted so that it remains closed.

The return liquid flows into the cylinder space 20 during the downward movement of the piston.
from the pipe 15, check valve 46, open valve 4
5, through chamber 47, line 2 and line 13 to cylinder space 16.

In this way, pressure liquid is thus supplied both from the pump 1 and from the cylinder space 20.

The effective piston area on which the pressure fluid from the pump acts is
It is equal to the difference between the two piston areas, i.e. the area of the piston rod.

Since the area of the piston rod is relatively small, the piston rod can be moved outward rapidly with small forces and adjusted for the low loads required when tilting the drive unit upwards.

The drive unit is lowered in the same sequence as described for the hydraulic device shown in FIG.

When trimming the drive unit while the boat is in motion, if a forward thrust force acts on the piston rod 35, more pressure must be created in the hydraulic system to overcome the reaction force.

The spring 42 is therefore adjusted to yield to the high pressure on the actuating piston 26 and open the valve 38.

During the downward movement of the piston 32, which tilts it in order to trim the drive unit, the liquid discharged from the cylinder space 20 will thus be passed to the tank via the opened valve 38.

Therefore, the connection through valve 45, which is still open,
It remains closed by 6.

Liquid is therefore passed into the cylinder space 16 only from the pump 1 and the pressure acts on the entire piston area, so that
Greater force results in slower piston movement.

The spring 42 of the actuating piston 26 can be adjusted to vary the opening pressure of the valve 38 in a manner not described in detail.

The hydraulic device therefore automatically adjusts to rapid piston movement with low forces and slow piston movement with high forces, depending on the pressure within it.

An embodiment comprising a device for manually making the aforementioned adjustments will now be described with reference to Figures 3 and 4.5.

FIG. 3 shows only part of the hydraulic device for controlling the movement of the piston 32, the remaining parts fully matching the device of FIG.

That is, the control valve 12 is included.

In the illustrated embodiment, the previously mentioned check valve 27 is replaced by a valve 50 which, in addition to the check function, also performs the switching operation described above, thereby providing rapid piston movement with low forces. Or perform either a slow piston movement with a large force.

The valve 50 comprises a rotatable valve element 51, which is connected to the gear mechanism of the drive by means of a null motion mechanism (FIG. 5), so that it can be moved into an advanced position, a retracted position and a neutral position. An adjustment between also results in an adjustment of the valve element 51.

In the illustrated embodiment, the idle motion mechanism is constituted by an actuation arm 56 with a slot 55 and a stud 57, the stud 57 being rigidly connected to the valve element 51 and engaging within the slot 55. The slots are sized so that the actuation arm 56 makes a 30 degree idle movement before the valve element 51 is moved by the stud.

The actuation arm 56 is connected to the gear mechanism via a connection 58, for example in the form of a Bowden cable.

By using the null motion mechanism, two different positions of the valve element 51 are obtained with respective neutral positions of the gear mechanism and the actuating arm 56.

That is, a first neutral position in the adjustment from forward to neutral and a second neutral position in the adjustment from reverse to neutral are obtained.

Different positions of the valve element 51 are shown in FIGS. 4a4d.

In the position shown in FIG. 4a, the cylinder space 20 communicates with the tank 6 through the passage 53 of the valve element and the line 15, and the gear mechanism is in position for forward movement of the boat.

The hydraulic system is now adjusted so that the drive unit can be trimmed.

Figure 4b shows a first neutral position achieved by adjusting the actuation arm 56 connected to the valve element 51 with a null movement of 30 to 60 degrees.

Thus, the valve element 51 is adjusted over 30 degrees but still communicates the cylinder space 20 with the tank, so that the hydraulic device is still set for trimming.

Continuing to adjust the actuating arm 56 by 60 degrees toward the retracted position, the valve element 51 is adjusted by 60 degrees and the fourth
As shown in Figure c, the discharge pipe line from the cylinder space 20 is closed.

This corresponds to a check position that prevents the drive unit from being tilted upwards by rear-acting propulsion forces when the boat is reversing, as described above.

Finally, when the actuation arm is reset to the neutral position by 60 degrees, the valve element 51 is adjusted to the second neutral position by 30 degrees.

In this position the valve has two cylinder spaces 16, 2
1 are connected to each other through passage 54, passage 53 and short-circuit line 52 in an upwardly inclined position of the drive unit.

This results in the aforementioned rapid piston movement under small forces.

It goes without saying that with the present invention, space can be reduced compared to conventional systems that have both a double-acting cylinder device and a single-acting cylinder device.
The double-acting cylinder system and the automatic pressure actuator provide the advantage of being able to perform low-speed, high-force trimming and high-speed, low-force control of tilting motions, as in the prior art.

[Brief explanation of the drawing]

FIG. 1 is a circuit diagram of a known hydraulic device with two hydraulic cylinders, FIG. 2 is a circuit diagram of a hydraulic device according to the invention with a self-adjusting valve device, and FIG. 3 is a manual-adjustable circuit diagram. FIGS. 4a to 4d are schematic diagrams showing different positions of the manually adjustable valve arrangement; FIG. 4d is a schematic side view showing the switching mechanism for the valve arrangement shown in FIG. 1... pump, 6... tank, 11,
12...Control valve, 17...Double acting hydraulic cylinder, 16°20...Cylinder space, 27
..... Closing valve, 29 .... Overload valve, 30 .... Overload valve, 32 ....
Piston, 35...Piston rod.

Claims (1)

[Scope of utility model registration request] A hydraulic device for controlling the trimming and tilting movement of a hydraulic tilting propeller drive unit for a boat, the part comprising a piston rond and a cylinder having a piston therein, a part of the tiltable propeller drive unit and a fixed part of the boat. a hydraulic device comprising: a double-acting piston-cylinder device connected to; a tank; and a reversible pump connected to the cylinder space on the opposite side of the cylinder from the piston rond, for delivering a pressure medium from the tank to the cylinder; and a valve device that can be switched between a first position in which the cylinder space on the piston rod side of the cylinder communicates with the cylinder space on the opposite side and a second position in which the cylinder space on the piston rod side of the cylinder communicates with the tank. and the valve arrangement includes a pressure actuation device for automatically switching between the first and second positions in response to the pressure of the medium within the hydraulic device, the pressure actuation device including a piston. In response to the pressure in the hydraulic device being below the predetermined pressure as a result of a low load on the rod side, the valve device is switched to a first position to remove the opposite side of the piston rod from the cylinder space on the pump and piston rod side. A pressure medium is supplied to the side cylinder space, and when the pressure exceeds a predetermined value in response to a predetermined load or more on the piston rond in the hydraulic device, the valve device is switched to the second position to supply the pressure medium. A hydraulic device characterized in that it is configured to supply pressure medium only from a pump to a cylinder space on the opposite side of a piston rond, and to return pressure medium from the cylinder space on the piston rond side to a tank.