JP2006137225A - Hydraulic unit of outboard motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress increases in the number of parts and weight without requiring an exclusive driving source for driving a hydraulic pump, and make an output of a hydraulic actuator be freely adjusted in a hydraulic device of an outboard motor equipped with the hydraulic actuator driving a movable member of the outboard motor and a hydraulic pump supplying hydraulic oil to the hydraulic actuator. <P>SOLUTION: The hydraulic pump (40) is driven by the output of an engine driving a propeller, and the hydraulic circuit (38) connecting the hydraulic pump with a hydraulic cylinder (36) for steering is composed of first and second supply paths (38a, 38b) where the hydraulic oil supplied to first and second oil chambers (36c, 36d) of a hydraulic cylinder for steering passes, a first and second discharged paths (38c, 38d) where the hydraulic oil discharged from the first and second oil chambers passes, a supply oil quantity regulating valve (38e) disposed in a first and second supplying paths, and a discharged oil quantity regulating valve (38g) disposed in the first and second discharged paths. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a hydraulic device for an outboard motor, and more particularly to a hydraulic device for an outboard motor in which a movable member provided in the outboard motor is driven by a hydraulic actuator.

Conventionally, a technique in which a movable member such as a swivel shaft or a tilting shaft provided in an outboard motor is driven by a hydraulic actuator is known (for example, see Patent Document 1). In order to operate the hydraulic actuator, a hydraulic pump that supplies hydraulic oil to the hydraulic actuator is required. Therefore, when the movable member is driven by a hydraulic actuator, a dedicated drive source (in many cases, an electric motor) for driving the hydraulic pump is generally mounted separately from the engine that drives the propeller.
Japanese Patent Laid-Open No. 6-127475 (paragraphs 0014 to 0016, FIG. 1, etc.)

  However, when a drive source dedicated to the hydraulic pump is mounted as in the prior art, there is a problem that the number of parts and the weight of the outboard motor are increased.

  The above-described problems can be solved by driving the hydraulic pump by the output of the engine that drives the propeller. However, with such a configuration, the amount of hydraulic oil discharged from the hydraulic pump depends on the engine speed, and the problem arises that the output of the hydraulic actuator cannot be adjusted arbitrarily.

  Therefore, the present invention provides an exclusive drive source for driving a hydraulic pump in an outboard motor hydraulic apparatus including a hydraulic actuator that drives a movable member of the outboard motor and a hydraulic pump that supplies hydraulic oil to the hydraulic actuator. The purpose is to make the output of the hydraulic actuator adjustable while suppressing the increase in the number of parts and weight.

  In order to solve the above-mentioned object, in claim 1, an engine that drives a propeller of an outboard motor, a hydraulic pump that is driven by the output of the engine and discharges hydraulic oil, and a discharge from the hydraulic pump. A hydraulic actuator that has first and second oil chambers to which the supplied hydraulic oil is supplied and that drives a movable member of the outboard motor in accordance with the hydraulic oil supplied to the first and second oil chambers And a hydraulic circuit that connects the hydraulic pump and the hydraulic actuator, and the hydraulic circuit passes through the first and second hydraulic oil supplied to the first and second oil chambers. A supply path, first and second discharge paths through which hydraulic oil discharged from the first and second oil chambers passes, and a flow rate of the hydraulic oil disposed in the first and second supply paths To adjust the supply oil amount adjustment valve and And was configured to have a discharge oil amount adjusting valve for adjusting the flow rate of the hydraulic fluid disposed in said first and second discharge paths.

  According to a second aspect of the present invention, further, an engine speed detecting means for detecting the engine speed, and the supply oil amount adjusting valve and the discharged oil amount adjustment based on the detected engine speed. And a valve opening degree adjusting means for adjusting the opening degree of the valve.

  In the hydraulic apparatus for an outboard motor according to claim 1, a hydraulic pump that is driven by an output of an engine that drives a propeller to discharge hydraulic oil, and first and second oil chambers to which the hydraulic oil is supplied. And a hydraulic actuator that drives the movable member of the outboard motor in accordance with the hydraulic oil supplied to the first and second oil chambers. A drive source becomes unnecessary, and an increase in the number of parts and weight can be prevented.

  In addition, a hydraulic circuit connecting the hydraulic pump and the hydraulic actuator includes first and second supply paths through which hydraulic oil supplied to the first and second oil chambers of the hydraulic actuator passes, and first and second A first and second discharge passage through which hydraulic oil discharged from the oil chamber passes, a supply oil amount adjustment valve that adjusts the flow rate of the hydraulic oil disposed in the first and second supply passages, and a first And a discharge oil amount adjustment valve that adjusts the flow rate of the hydraulic oil disposed in the second discharge passage, and adjusts the opening of the supply oil amount adjustment valve and the discharge oil amount adjustment valve. The amount of hydraulic oil supplied to each oil chamber of the hydraulic actuator can be adjusted by this, so that even when a dedicated drive source for driving the hydraulic pump is not used, the output of the hydraulic actuator can be adjusted. It becomes possible.

  Further, in the present invention, the engine speed detecting means for detecting the engine speed, and the opening amounts of the supply oil amount adjusting valve and the discharged oil amount adjusting valve based on the detected engine speed are set. In addition to the above-described effect, the output of the hydraulic actuator can be prevented from fluctuating with the fluctuation of the engine speed.

  The best mode for carrying out the outboard motor hydraulic system according to the present invention will be described below with reference to the accompanying drawings.

  FIG. 1 is a schematic view showing an outboard motor hydraulic apparatus according to a first embodiment of the present invention together with a hull, and FIG. 2 is a partial side view of FIG.

  1 and 2, reference numeral 10 indicates an outboard motor. As shown in FIG. 2, the outboard motor 10 is housed rotatably in a stern bracket 14 fixed to the rear portion of the hull (ship) 12, a swivel case 16 attached to the stern bracket 14, and the swivel case 16. And a swivel shaft 18 (movable member).

  The upper end of the swivel shaft 18 is fixed to the frame of the outboard motor 10 via the mount frame 20. The lower end of the swivel shaft 18 is also fixed to the frame of the outboard motor 10 via a connecting member (not shown).

  The swivel case 16 is attached to the stern bracket 14 via a tilting shaft 22 (movable member). As a result, the outboard motor 10 is rotatable about the vertical axis with respect to the hull 12 using the swivel shaft 18 as a rotation axis (that is, can be steered to the left and right) and the horizontal axis with the tilting shaft 22 as a rotation axis. It can be rotated around (that is, the tilt trim angle can be adjusted).

  A propeller 24 is disposed at the lower part of the outboard motor 10. On the other hand, an engine 26 for driving the propeller 24 is mounted on the outboard motor 10. The engine 26 is a spark ignition type in-line four cylinder, which is a four-cycle gasoline engine having a displacement of 2200 cc. The output of the engine 26 is transmitted to a propeller shaft 32 via a drive shaft (vertical shaft) 28 connected to a crankshaft (not shown) and a shift mechanism 30. The propeller 24 rotates with the propeller shaft 32 and generates a thrust force that moves the hull 12 forward or backward.

  A crank angle sensor 34 is disposed near the crankshaft of the engine 26. The crank angle sensor 34 outputs a pulse signal for each predetermined crank angle.

  Above the swivel case 16, a hydraulic actuator that drives the swivel shaft 18 to adjust the steering angle of the outboard motor 10, more specifically, a double-acting hydraulic cylinder (hereinafter referred to as "steering hydraulic cylinder"). 36 is arranged. The steering hydraulic cylinder 36 is connected to a hydraulic pump 40 via a hydraulic circuit 38. The hydraulic pump 40 is driven by the output of the engine 26.

  Further, in the vicinity of the stern bracket 14 and the swivel case 16, a hydraulic actuator that drives the tilting shaft 22 to adjust the tilt trim angle of the outboard motor 10, specifically, a known power tilt trim unit 44. Is placed.

  As shown in FIG. 1, a steering wheel 46 is disposed near the cockpit of the hull 12. A rotation sensor 48 is attached to the rotation shaft of the steering wheel 46. The rotation sensor 48 outputs a signal corresponding to the rotation angle of the steering wheel 46 operated by the operator.

  A shift lever 50 and a throttle lever 52 are further arranged near the cockpit. The shift lever 50 and the throttle lever 52 are connected to the shift mechanism 30 and a throttle valve (not shown) of the engine 26 via push-pull cables, respectively. That is, when the shift lever 50 is operated by the operator, the shift mechanism 30 operates and the traveling direction of the hull 12 is switched. Further, when the throttle lever 52 is operated, the throttle valve opens and closes, the engine speed is adjusted, and the ship speed of the hull 12 is adjusted.

  Further, a power tilt trim switch 54 for inputting an instruction for adjusting the tilt trim angle of the outboard motor 10 is disposed near the cockpit. Specifically, the power tilt trim switch 54 includes a seesaw switch having an up side and a down side, and outputs a signal corresponding to a tilt trim angle increase / decrease instruction input from the operator.

  The outputs of the crank angle sensor 34, the rotation sensor 48, and the power tilt trim switch 54 are input to an ECU (Electronic Control Unit) 56 disposed near the engine 26. The ECU 56 is composed of a microcomputer including a CPU, a ROM, a RAM, and a counter.

  The ECU 56 counts the pulse signal output from the crank angle sensor 34 to detect (calculate) the engine speed, and the oil provided in the hydraulic circuit 38 based on the detected engine speed and the output of the rotation sensor 48. The amount of hydraulic fluid supplied to the steering hydraulic cylinder 36 is adjusted by adjusting the opening of a quantity adjusting valve (described later). The ECU 56 controls the drive of the power tilt trim unit 44 based on the output of the power tilt trim switch 54.

  FIG. 3 is an enlarged partial sectional view of the vicinity of the swivel case 16 shown in FIG.

  As shown in FIG. 3, the power tilt trim unit 44 includes one hydraulic cylinder for tilt angle adjustment (hereinafter referred to as “tilt hydraulic cylinder”) 44a and two (only one is shown in the figure). A trim angle adjusting hydraulic cylinder (hereinafter referred to as “trim hydraulic cylinder”) 44b is integrally provided. The tilt hydraulic cylinder 44a and the trim hydraulic cylinder 44b are both double-acting hydraulic cylinders.

  The cylinder bottom of the tilt hydraulic cylinder 44 a is connected to the stern bracket 14, and the rod head is connected to the swivel case 16. The trim hydraulic cylinder 44 b has a cylinder bottom connected to the stern bracket 14 and a rod head abutted against the swivel case 16. As a result, the tilt hydraulic cylinder 44a or the trim hydraulic cylinder 44b is driven to rotate the swivel case 16 about the tilting shaft 22 as a rotation axis, and thus the tilt trim angle of the outboard motor 10 is adjusted.

  FIG. 4 is a plan view of the vicinity of the swivel case 16.

  As shown in FIGS. 3 and 4, a stay 60 is provided in the mount frame 20 in the vicinity of the position immediately above the swivel shaft 18. The steering hydraulic cylinder 36 has a piston rod head 36 a connected to the stay 60 and a cylinder bottom 36 b connected to the swivel case 16. As a result, the steering hydraulic cylinder 36 is driven to rotate the swivel shaft 18 together with the stay 60 and the mount frame 20, and thus the outboard motor 10 is steered left and right.

  FIG. 5 is an explanatory diagram showing the steering hydraulic cylinder 36, the hydraulic circuit 38, and the hydraulic pump 40 shown in FIG.

  The hydraulic pump 40 is a known gear pump, and as shown in FIG. 5, a drive shaft 40a, a suction port 40b that sucks hydraulic oil when the drive shaft 40a is driven, and a discharge that discharges the sucked hydraulic oil. And an outlet 40c. The drive shaft 40a is driven by transmitting the rotation of the drive shaft 28 described above. Transmission of power from the drive shaft 28 to the drive shaft 40a may be performed by a speed reduction mechanism or the like, or the drive shaft 40a itself may form part of the drive shaft 28.

  As described above, the steering hydraulic cylinder 36 is a double-acting hydraulic cylinder, and includes a first oil chamber 36c and a second oil chamber 36d to which hydraulic oil discharged from the hydraulic pump 40 is supplied. A piston 36e is interposed between the first oil chamber 36c and the second oil chamber 36d. As described above, the rod head 36 a of the piston 36 e is connected to the stay 60 provided on the mount frame 20. Therefore, the piston 36e is displaced according to the hydraulic oil supplied to the first and second oil chambers 36c and 36d, so that the swivel shaft 18 is rotated together with the stay 60 and the mount frame 20.

  The hydraulic circuit 38 includes a first supply path (oil path) 38a through which hydraulic oil supplied to the first oil chamber 36c of the steering hydraulic cylinder 36 passes and hydraulic oil supplied to the second oil chamber 36d. Is discharged from the second supply passage (oil passage) 38b through which the hydraulic fluid passes, the first discharge passage (oil passage) 38c through which the hydraulic oil discharged from the first oil chamber 36c passes, and the second oil chamber 36d. And a second discharge path (oil path) 38d through which the hydraulic oil passes.

  In the first supply path 38a and the second supply path 38b, a supply oil amount adjustment valve 38e for adjusting the flow rate of the hydraulic oil passing therethrough is disposed. The supply oil amount adjusting valve 38e includes a first valve body 38e1 that adjusts the flow passage area of the first supply passage 38a, and a second valve body 38e2 that adjusts the flow passage area of the second supply passage 38b. Prepare. As shown in the figure, the first valve body 38e1 and the second valve body 38e2 are rotary throttle valves, and their rotary shafts are connected and driven by one electromagnetic solenoid 38f. The first valve body 38e1 and the second valve body 38e2 have an opening degree that is inversely proportional (that is, the opening degree of the second valve body 38e2 increases as the opening degree of the first valve body 38e1 increases). A predetermined phase difference, specifically a phase difference of 90 degrees, is provided so that the second valve body 38e2 increases as the opening degree of the first valve body 38e1 decreases.

  In addition, the first and second discharge passages 38c and 38d are also provided with a discharge oil amount adjusting valve 38g that adjusts the flow rate of hydraulic oil passing therethrough. The discharged oil amount adjusting valve 38g includes a first valve body 38g1 that adjusts the flow path area of the first discharge path 38c, and a second valve body 38g2 that adjusts the flow path area of the second discharge path 38d. Prepare. The first valve body 38g1 and the second valve body 38g2 are also rotary throttle valves, and their rotary shafts are connected and driven by a single electromagnetic solenoid 38h, and the opening degree is set in inverse proportion. A phase difference of (90 degrees) is provided.

  The first supply path 38a and the second supply path 38b are combined with a single oil path (indicated by reference numeral 38ab) on the upstream side (side closer to the hydraulic pump 40) than the supply oil amount adjustment valve 38e. It is connected to the discharge port 40 c of the pump 40. In the oil passage 38ab, a check valve 38i that allows only the flow of hydraulic oil from the discharge port 40c of the hydraulic pump 40 toward the oil chambers 36c and 36d of the hydraulic actuator 36 is disposed.

  Further, the first discharge path 38c and the second discharge path 38d are merged into one oil path (indicated by reference numeral 38cd) on the downstream side (side closer to the hydraulic pump 40) than the discharged oil amount adjusting valve 38g. , Connected to the suction port 40b of the hydraulic pump 40. In the oil passage 38cd, a check valve 38j that permits only the flow of hydraulic oil from the oil chambers 36c, 36d of the hydraulic actuator 36 toward the suction port 40b of the hydraulic pump 40 is disposed.

  Furthermore, the upstream side of the check valve 38i of the oil passage 38ab and the downstream side of the check valve 38j of the oil passage 38cd are connected by an oil passage 38k. In the oil passage 38k, a check valve 38m that permits only the flow of hydraulic oil from the oil passage 38ab to the oil passage 38cd is disposed.

  Further, the first supply path 38a and the first discharge path 38c are merged into one oil path in the vicinity of the steering hydraulic cylinder 36 and connected to the first oil chamber 36c. The second supply path 38a and the second discharge path 38d are also merged into one oil path in the vicinity of the steering hydraulic cylinder 36 and connected to the second oil chamber 36d.

  Next, the flow of the hydraulic oil will be described. The hydraulic oil discharged from the discharge port 40c of the hydraulic pump 40 passes through the check valve 38i of the oil path 38ab and passes through the first supply path 38a and the second supply path 38b. Is flowed into. The hydraulic fluid that has flowed into the first supply path 38a and the second supply path 38b passes through the supply oil amount adjustment valve 38e and enters the first oil chamber 36c and the second oil chamber 36d of the steering hydraulic cylinder 36. Supplied.

  On the other hand, the hydraulic oil discharged from the first oil chamber 36c and the second oil chamber 36d of the steering hydraulic cylinder 36 flows into the first discharge path 38c and the second discharge path 38d, respectively. The hydraulic oil that has flowed into the first discharge path 38c and the second discharge path 38d passes through the discharge oil amount adjustment valve 38g and flows into the oil path 38cd, and then passes through the check valve 38j and passes through the hydraulic pump 40. Is returned to the suction port 40b.

  Here, the amount of hydraulic oil flowing from the oil passage 38ab into the first supply passage 38a and the second supply passage 38b is determined according to the opening degree of the valve bodies 38e1 and 38e2 of the supply oil amount adjustment valve 38e. The That is, the hydraulic oil discharged from the hydraulic pump 40 is distributed to the first supply path 38a and the second supply path 38b according to the opening ratio of the valve bodies 38e1 and 38e2 of the supply oil amount adjustment valve 38e. The oil is supplied to the first oil chamber 36c and the second oil chamber 36d of the steering hydraulic cylinder 36.

  Therefore, as shown in FIG. 5, if the opening degrees of the valve bodies 38e1 and 38e2 of the supply oil amount adjustment valve 38e coincide with each other, the first oil chamber 36c and the second oil chamber 36d are operated in the same amount. Oil is supplied and the piston 36e is not displaced. At this time, the opening degrees of the valve bodies 38g1 and 38g2 of the discharged oil amount adjusting valve 38g are made to coincide with each other, and the surplus hydraulic fluid is supplied to the suction port of the hydraulic pump 40 through the discharge paths 38c and 38d and the oil path 38cd. Reflux to 40b. When the oil pressure acting on the oil passage 38ab exceeds a predetermined value, the check valve 38m disposed in the oil passage 38k is opened, and the oil passage 38ab and the oil passage 38cd are communicated to release the oil pressure. In FIG. 5, the flow of hydraulic oil supplied to the oil chambers 36c and 36d is indicated by solid arrows, and the flow of hydraulic oil returned to the hydraulic pump 40 is indicated by broken arrows.

  On the other hand, as shown in FIG. 6, the first valve body 38e1 of the supply oil amount adjustment valve 38e is closed, the second valve body 38e2 is opened, and the first of the discharged oil amount adjustment valve 38g is opened. When the valve body 38g1 is opened and the second valve body 38g2 is closed, the hydraulic oil passes through the second supply path 38b and is supplied only to the second oil chamber 36d of the steering hydraulic cylinder 36. . As a result, the piston 36e is displaced upward in the figure. Further, the hydraulic oil is discharged from the first oil chamber 36c. The hydraulic oil discharged from the first oil chamber 36c passes through the first discharge path 36c and the oil path 38cd and is returned to the hydraulic pump 40.

  On the other hand, as shown in FIG. 7, the first valve body 38e1 of the supply oil amount adjustment valve 38e is opened, the second valve body 38e2 is closed, and the first valve body of the discharged oil amount adjustment valve 38g. By closing the valve 38g1 and opening the second valve body 38g2, the hydraulic oil passes through the first supply path 38a and is supplied only to the first oil chamber 36c of the steering hydraulic cylinder 36. As a result, the piston 36e is displaced downward in the drawing, and the hydraulic oil is discharged from the second oil chamber 36d. The hydraulic fluid discharged from the second oil chamber 36d passes through the second discharge passage 36d and the oil passage 38cd and is returned to the hydraulic pump 40.

  Thus, the opening degree of the supply oil amount adjusting valve 38e disposed in the first supply path 38a and the second supply path 38b, and the discharge disposed in the first discharge path 38c and the second discharge path 38d. The steering hydraulic cylinder 36 can be driven by adjusting the opening of the oil amount adjusting valve 38g.

  It should be noted that the opening ratio of each valve body provided in the oil amount adjusting valves 38e, 38g (specifically, the opening ratio between the first valve body 38e1 and the second valve body 38e2 of the supply oil amount adjusting valve 38e). The difference or the opening difference between the first valve body 38g1 and the second valve body 38g2 of the discharged oil amount adjusting valve 38g), in other words, the first oil chamber 36c and the second oil chamber 36d. By adjusting the distribution ratio of the hydraulic fluid supplied to, the driving speed of the steering hydraulic cylinder 36 (displacement speed of the piston 36e) can be changed.

  Next, opening control of the supply oil amount adjustment valve 38e and the discharged oil amount adjustment valve 38g will be described. FIG. 8 is a flowchart showing the control process. The illustrated program is executed in the ECU 56 at a predetermined cycle.

  In the following, first, in S10, the opening degree (basic value) of the supply oil amount adjustment valve 38e and the discharged oil amount adjustment valve 38g is determined based on the output of the rotation sensor 48, that is, the rotation angle of the steering wheel 46. Specifically, the opening degree of each valve body provided in the supply oil amount adjustment valve 38e and the discharged oil amount adjustment valve 38g is determined.

  Next, in S12, the opening degrees of the supply oil amount adjustment valve 38e and the exhaust oil amount adjustment valve 38g are corrected based on the engine speed. As described above, the hydraulic pump 40 is driven by the output of the engine 26 together with the propeller 24. Accordingly, the amount of hydraulic oil discharged from the hydraulic pump 40 depends on the engine speed. For this reason, when the engine speed fluctuates with the adjustment of the boat speed or the like, the output of the steering hydraulic cylinder 36 also fluctuates.

  Therefore, in S12, the above-described problems are solved by correcting the opening of each oil amount adjusting valve 38e, 38g based on the engine speed. Specifically, as the engine speed increases (the hydraulic oil discharge flow rate increases and the hydraulic pressure supplied to the steering hydraulic cylinder 36 increases), each valve element provided in the oil amount adjustment valves 38e and 38g. Of the first oil chamber 36c and the second oil chamber 36d is corrected in the decreasing direction.

  As a result, even if the supply hydraulic pressure fluctuates as the engine speed fluctuates, the pressure difference between the first oil chamber 36c and the second oil chamber 36d can be kept constant. Variations in the output of the cylinder 36 can be prevented.

  If the explanation of the flowchart of FIG. 8 is continued, the process proceeds to S14, and the drive of the electromagnetic solenoids 38f, 38h is controlled so that the oil amount adjusting valves 38e, 38g have the opening obtained by correcting in S12. Specifically, an energization command value is calculated based on the opening obtained by correcting in S12, and the calculated energization command value is output to the electromagnetic solenoids 38f and 38h via an output circuit (not shown).

  Thus, in the hydraulic apparatus for an outboard motor according to the first embodiment of the present invention, the hydraulic pump 40 that is driven by the output of the engine 26 that drives the propeller 24 and discharges hydraulic oil, Since the steering hydraulic cylinder 36 that drives the swivel shaft 18 that is a movable member is provided according to the hydraulic oil supplied to the second oil chambers 36c and 36d, a dedicated drive for driving the hydraulic pump 40 is provided. A source becomes unnecessary, and the number of parts and weight can be reduced.

  The hydraulic circuit 38 that connects the hydraulic pump 40 and the steering hydraulic cylinder 36 has first and second hydraulic oil supplied to the first and second oil chambers 36c and 36d of the steering hydraulic cylinder 36 passing therethrough. Supply passages 38a and 38b, first and second discharge passages 38c and 38d through which hydraulic oil discharged from the first and second oil chambers 36c and 36d passes, and first and second supply passages 38a. , 38b and the discharged oil amount adjusting valve 38g disposed in the first and second discharge passages 38c, 38d, the supplied oil amount adjusting valve 38e, The amount of hydraulic oil supplied to each of the oil chambers 36c and 36d can be adjusted by adjusting the opening of the discharged oil amount adjusting valve 38g, and therefore, the hydraulic pump 40 is not driven by a dedicated drive source. Even steering It is possible to adjust the output of the hydraulic cylinder 36.

  Further, since the engine speed is detected and the opening degrees of the supply oil amount adjusting valve 36e and the discharged oil amount adjusting valve 36g are adjusted based on the detected engine speed, in addition to the above effect, the engine speed It is possible to prevent the fluctuation of the number from affecting the output of the steering hydraulic cylinder 36.

  As described above, in the first embodiment of the present invention, the engine (26) that drives the propeller (24) of the outboard motor (10) and the hydraulic oil driven by the output of the engine (26) are used. The hydraulic pump (40) that discharges and the first and second oil chambers (36c, 36d) to which the hydraulic oil discharged from the hydraulic pump (40) is supplied, and the first and second oils A hydraulic actuator (steering hydraulic cylinder 36) for driving the movable member (swivel shaft 18) of the outboard motor (10) in accordance with hydraulic oil supplied to the chambers (36c, 36d), and the hydraulic pump (40 ) And a hydraulic circuit (38) for connecting the hydraulic actuator (36), and the hydraulic circuit (38) is supplied to the first and second oil chambers (36c, 36d). Pass First and second supply passages (38a, 38b) and first and second discharge passages (38c, 38d) through which hydraulic oil discharged from the first and second oil chambers (36c, 36d) passes. ), A supply oil amount adjusting valve (38e) for adjusting the flow rate of the hydraulic oil disposed in the first and second supply passages (38a, 38b), and the first and second discharge passages ( 38c, 38d) and a discharged oil amount adjusting valve (38g) for adjusting the flow rate of the hydraulic oil.

  Further, engine speed detecting means (crank angle sensor 34) for detecting the speed of the engine (26), and the supply oil amount adjusting valve (38e) and the discharged oil based on the detected engine speed. Valve opening adjustment means (electromagnetic solenoid 38f, electromagnetic solenoid 38h, ECU 56, S12, S14 in the flowchart of FIG. 8) for adjusting the opening of the amount adjustment valve (38g) is provided.

  In the above description, the swivel shaft 18 is exemplified as the movable member of the outboard motor 10. However, the tilting shaft 22 and other members (not shown) may be used.

  Further, although the hydraulic actuator to be used is a hydraulic cylinder, it may be a hydraulic motor or the like.

  In addition, the two valve bodies 38e1 and 38e2 provided in the supply oil amount adjusting valve 38e are connected and driven by one electromagnetic solenoid 38f. However, the individual solenoid solenoids are not connected without connecting each valve body. You may make it drive with. Further, the actuator for driving the valve bodies 38e1 and 38e2 is not limited to the electromagnetic solenoid 38f, and other actuators such as an electric motor may be used. Furthermore, although the valve bodies 38e1 and 38e2 are rotary throttle valves, other types such as a direct-acting throttle valve may be used. The same applies to the discharged oil amount adjustment valve 38g.

1 is a schematic view showing an outboard motor hydraulic apparatus according to a first embodiment of the present invention together with a hull. It is a partial explanatory side view of the apparatus shown in FIG. FIG. 3 is an enlarged partial sectional view in the vicinity of a swivel case shown in FIG. 2. FIG. 3 is a plan view of the vicinity of a swivel case shown in FIG. 2. It is explanatory drawing showing the hydraulic cylinder for steering shown in FIG. 2, a hydraulic circuit, and a hydraulic pump. FIG. 6 is an explanatory view similar to FIG. 5, showing the steering hydraulic cylinder, the hydraulic circuit, and the hydraulic pump shown in FIG. 2. FIG. 6 is an explanatory view similar to FIG. 5, showing the steering hydraulic cylinder, the hydraulic circuit, and the hydraulic pump shown in FIG. 2. It is a flowchart showing the opening degree control processing of the supply oil amount adjustment valve and the discharge oil amount adjustment valve shown in FIG.

Explanation of symbols

10 Outboard motor 18 Swivel shaft (movable member)
24 propeller 26 engine 34 crank angle sensor (engine speed detection means)
36 Steering hydraulic cylinder (hydraulic actuator)
36c 1st oil chamber 36b 2nd oil chamber 38 Hydraulic circuit 38a 1st supply path 38b 2nd supply path 38c 1st discharge path 38d 2nd discharge path 38e Supply oil amount adjustment valve 38f Electromagnetic solenoid (valve Opening adjustment means)
38g Discharged oil amount adjustment valve 38h Electromagnetic solenoid (valve opening adjustment means)
40 Hydraulic pump 56 ECU (valve opening adjusting means)

Claims (2)

a. An engine that drives the propeller of the outboard motor,
b. A hydraulic pump driven by the output of the engine to discharge hydraulic oil;
c. The movable member of the outboard motor includes first and second oil chambers to which hydraulic oil discharged from the hydraulic pump is supplied, and according to the hydraulic oil supplied to the first and second oil chambers. A hydraulic actuator for driving
And d. A hydraulic circuit connecting the hydraulic pump and the hydraulic actuator;
And the hydraulic circuit comprises:
e. First and second supply passages through which hydraulic oil supplied to the first and second oil chambers passes;
f. First and second discharge passages through which hydraulic oil discharged from the first and second oil chambers passes;
g. A supply oil amount adjustment valve that adjusts the flow rate of the hydraulic oil disposed in the first and second supply paths;
And h. A discharge oil amount adjusting valve for adjusting a flow rate of the hydraulic oil disposed in the first and second discharge passages;
An outboard motor hydraulic system comprising: further,
i. Engine speed detecting means for detecting the engine speed;
And j. Valve opening degree adjusting means for adjusting the opening degree of the supply oil amount adjusting valve and the discharged oil amount adjusting valve based on the detected engine speed;
The outboard motor hydraulic system according to claim 1, further comprising:

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