JP2922613B2 - Switching valve device of hydraulic clutch for ship propulsion - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a switching valve device for a hydraulic clutch for a marine propulsion device.

[Prior Art] Conventionally, as described in Japanese Utility Model Publication No. 59-4879, the rotational force of an engine is transmitted to the propeller shaft side via a hydraulic clutch, and the propeller shaft is shifted to neutral, forward, and reverse operation states. There is something to do.

At this time, the hydraulic clutch is additionally provided with a switching valve device as shown in FIG. This switching valve device has a ninth
As shown in the figure, a stem valve 2 is disposed in a housing 1 and a shift lever 3A provided on an operating portion 2A of the stem valve 2.
The stem valve 2 is rotatable around its own axis by an operating force applied to the stem valve 2. Oil extending from one end pressure receiving surface 2B crossing the own axis of the stem valve 2 to an oil distribution outer peripheral surface 2C formed on the outer peripheral portion of the stem valve 2 The supply path 3 is bored in the stem valve 2. An oil discharge passage 4 is provided at a portion of the housing 1 facing the pressure receiving surface 2B of the stem valve 2.
A forward oil passage 5 communicating with the forward hydraulic clutch and a reverse oil passage 6 communicating with the reverse hydraulic clutch are opened at a portion of the housing 1 facing the oil distribution outer peripheral surface 2C of the stem valve 2. . Thereby, in this switching valve device, the high pressure supplied from the oil discharge passage 4 is provided by selectively communicating the oil supply passage 3 with the forward oil passage 5 and the reverse oil passage 6 by rotating the stem valve 2. The oil is selectively distributed to the forward hydraulic clutch and the reverse hydraulic clutch.

The forward hydraulic clutch to which the high-pressure oil is distributed transmits the rotational force of the engine to the propeller shaft side so as to rotate the propeller forward, and the reverse hydraulic clutch to which the high-pressure oil is distributed causes the propeller to rotate backward. The engine torque is transmitted to the propeller shaft side.

[Problems to be Solved by the Invention] However, in the switching valve device as described above, the oil supply passage 3 of the stem valve 2 is pressure-fed from the oil pump.
The high-pressure oil filled therein exerts a radial force R (see FIGS. 10A to 10C) on the stem valve 2, and this radial force increases the rotational operation force of the stem valve 2 and reduces the shift operation force. It causes the disadvantage of making it heavier.

FIG. 10 (A) shows the oil supply path 3 of the stem valve 2.
Is in a reverse mode in which the oil supply passage 3 communicates with the reverse oil passage 6, and FIG. 10 (B) shows that the oil supply passage 3 of the stem valve 2 communicates with both the forward oil passage 5 and the reverse oil passage 6. FIG. 10C shows a state in which the radial force R is generated in the neutral mode in which no oil is supplied, and FIG. 10C shows a state in which the radial force R is generated in the forward mode in which the oil supply passage 3 of the stem valve 2 communicates with the forward oil passage 5.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a switching valve device for a hydraulic clutch for a marine propulsion device, in which the radial operation force acting on the stem valve is reduced to reduce the rotational operation force of the stem valve and reduce the shift operation force.

Means for Solving the Problems According to the present invention, a stem valve is provided in a housing, and the stem valve can be rotated around its own axis by an operating force applied to an operating portion of the stem valve. An oil supply passage extending from one pressure receiving surface crossing the axis to an oil distribution outer peripheral surface formed on the outer peripheral portion of the stem valve is formed in the stem valve, and an oil discharge passage is provided in a portion of the housing facing the pressure receiving surface of the stem valve. A forward oil passage communicating with a forward hydraulic clutch and a reverse oil passage communicating with a reverse hydraulic clutch are opened in a portion of the housing that faces the oil distribution outer peripheral surface of the stem valve in the housing. The supply passage is selectively communicated with the forward oil passage and the reverse oil passage, and the high-pressure oil supplied from the oil discharge passage is moved backward with the forward hydraulic clutch. In a switching valve device for a marine propulsion hydraulic clutch that can be selectively distributed to a hydraulic clutch for a ship, an oil balance path branched from an oil supply path is formed in a stem valve, and the oil balance path is provided with an oil on an outer peripheral portion of the stem valve. It is opened on the back side with respect to the supply path opening position, and is set so that the radial force exerted by the oil pressure in the oil supply path on the stem valve and the radial force exerted by the oil pressure in the oil balance path on the stem valve are balanced.

According to the present invention, by selecting the opening position and the opening area of the oil balance passage, the radial force exerted by the oil pressure in the oil supply passage on the stem valve and the radial force exerted by the oil passage in the oil balance passage on the stem valve are selected. The forces are set to be balanced, and both radial forces can be offset. Accordingly, in the switching valve device of the hydraulic clutch for a marine propulsion device, the rotational operation force of the stem valve is reduced by reducing the radial force acting on the stem valve,
Shift operation force can be reduced.

Since the shift operation force is reduced, the shift feeling is improved, the shift cable life is improved,
There are advantages such as a reduction in the number of shift adjustments and an improvement in the durability of shift-related components.

FIG. 1 is a sectional view showing an inboard / outboard motor to which the present invention is applied.
FIG. 2 is a side view showing the appearance of the inboard / outboard motor, FIG.
(B) is a circuit diagram showing an operation circuit of the hydraulic clutch, FIG. 4 is a cross-sectional view showing a switching valve device, FIG. 5 is a cross-sectional view taken along the line VV in FIG. 4, and FIGS. (C) is VI-VI in FIG.
7 is a sectional view showing a switching state of the switching valve device in a line, FIG. 7 is a sectional view showing a modification of the present invention, and FIG.
FIG. 9 is a cross-sectional view taken along the line VIII, FIG. 9 is a cross-sectional view showing a conventional switching valve device, and FIGS. 10 (A) to 10 (C) show the switching state of the switching valve device along line XX in FIG. It is sectional drawing.

As shown in FIGS. 1 and 2, the inboard / outboard motor 10 rotatably supports a gimbal ring 13 via a steering shaft to a gimbal housing 12 fixed to a hull 11, and The propulsion unit 14 is supported so as to be tiltable through the intermediary. That is, the propulsion unit 14 can be tilted up by tilting around the tilt axis. 10A is a pair of tilt cylinders.

 An engine 15 is installed inside the hull 11.

An input shaft 16 is disposed substantially horizontally on the upper part of the propulsion unit 14, and an engine is connected to a front end of the input shaft 16 via a universal joint 17.
Fifteen output shafts 18 are connected.

An intermediate shaft 20 connected to a propeller shaft 19 is disposed substantially vertically above and below the propulsion unit 14.

At this time, the gear 21 is fixed to the lower end of the intermediate shaft 20,
A gear 22 that is always meshed with the gear 21 is fixed to a front end of the propeller shaft 19. The propeller 23 is fixed to the rear end of the propeller shaft 19.

A driven gear 24 is fixed to the upper end of the intermediate shaft 20,
A forward gear 25 and a reverse gear 26 meshing with the driven gear 24 are supported at the front and rear of the central portion of the input shaft 16 so as to freely rotate.

The forward gear 25 around the center of the input shaft 16
A hydraulic clutch 27 that selectively couples the forward gear 25 and the reverse gear 26 to the input shaft 16 is provided between the hydraulic clutch 27 and the reverse gear 26.

Here, a clutch housing 28 is welded and joined around a center portion of the input shaft 16, a forward hydraulic clutch 27F is formed on the forward gear 25 side in the clutch housing 28, and the forward hydraulic clutch 27F is moved backward on the reverse gear 26 side in the clutch housing 28. Hydraulic clutch 27
R is formed.

At this time, the forward hydraulic clutch 27F is configured as follows. That is, a pressurizing chamber 29 is formed in the inner portion on the front side of the clutch housing 28 and the forward piston 30
Is stored. Further, inside the front side of the clutch housing 28, clutch plates 31 engaged with the clutch housing 28 and friction plates 32 spline-coupled to the forward gear 25 are alternately arranged. The clutch plate 31 located on the innermost side of the clutch housing 28 abuts on the forward piston 30, and the clutch plate 31 located on the front end side of the clutch housing 28 is a pressure plate fixed to the clutch housing 28. It is in contact with 33. The forward piston 30 is urged by the return spring 34 in a direction away from the clutch plate 31,
The return spring 34 is supported on the back by a spring receiving plate 35,
Reference numeral 35 denotes a back gear supported by the forward gear 25 via a thrust bearing. In the forward hydraulic clutch 27F, when the inboard / outboard motor 10 is moved forward, high-pressure oil is supplied to the pressurized portion 29.

The reverse hydraulic clutch 27R is configured as follows. That is, a pressurizing chamber 39 is formed in a rear inner portion of the clutch housing 28, and a reverse piston 40 is housed therein. A clutch plate 41 that engages with the clutch housing 28 is provided inside the rear side of the clutch housing 28.
And friction plates 42 that are spline-coupled to the reverse gear 26 are alternately arranged. The clutch plate 41 located on the innermost side of the clutch housing 28 contacts the reverse piston 40,
The clutch plate 41 located at the rearmost end of the clutch housing 28 is in contact with a pressure plate 43 fixed to the clutch housing 28. The reverse piston 40 is a return spring.
The return spring 44 is biased in a direction away from the clutch plate 41 by 44, the back surface of the return spring 44 is supported by a spring receiving plate 45, and the spring receiving plate 45 is supported by the reverse gear 26 via a thrust bearing. In this reverse hydraulic clutch 27R, the
When 0 is moved backward, high-pressure oil is supplied to the pressurizing chamber 39.

Further, a drive unit 50 for the hydraulic clutch 27 is connected to a rear end of the input shaft 16. The drive unit 50 is a propulsion unit
A rear opening 51R formed in the upper rear surface of the upper part 14 has a drive part housing 53 which is fitted and fixed in a liquid-tight manner with bolts 52. The drive part housing 53 has an oil pump 54 and a switching valve device.
Built-in 55.

Further, a hydraulic circuit as shown in FIGS. 3A and 3B is extended from the propulsion unit 14, the drive unit housing 53 and the input shaft 16.

That is, the oil pump 54 is a gear pump including a drive gear 54A that is driven by being connected to the rear end of the input shaft 16, and a driven gear 54B that meshes with the drive gear 54A. 54C is a cap. As a result, the oil pump 54
The oil sucked from the oil suction passage 56 extending from the propulsion unit 14 and the drive housing 53 so as to communicate with the gear housing chambers of the lower gears 21 and 22 is pressurized. In a state adjusted to an appropriate oil pressure, the oil is sent to a switching valve device 55 from an oil discharge passage 58 extending from the drive unit housing 53.

The switching valve device 55 has a stem valve 59 disposed in the housing 53, and automatically operates the stem valve 59 by a remote operation force applied via a cable or the like to a shift lever 60 connected to the operating shaft of the stem valve 59. It is possible to rotate around the axis. One end pressure receiving surface that intersects the axis of stem valve 59
An oil supply path 61 extending from 59B to an oil distribution outer peripheral surface 59C formed on the outer peripheral portion of the stem valve 59 is bored in the stem valve 59. The portion of the housing 53 facing the pressure receiving surface 59B of the stem valve 59 is provided with the oil discharge passage 5 described above.
8 and the forward hydraulic clutch 2 is provided on the portion of the housing 53 facing the oil distribution outer peripheral surface 59C of the stem valve 59.
A forward oil passage 64 communicating with 7F and a reverse oil passage 65 communicating with the reverse hydraulic clutch 27R are opened. The rotation of the stem valve 59 causes the oil supply passage 61 to move through the forward oil passage.
64 and the reverse oil passage 65 to selectively communicate with the oil discharge passage 58.
High-pressure oil supplied from the vehicle is selectively distributed to the forward hydraulic clutch 27F and the reverse hydraulic clutch 27R, and as a result, the following neutral modes (1) to (3) can be established: neutral mode, forward mode, or reverse mode. I do. The stem valve 59 includes an oil discharge passage 63 extending from the housing 53 and the propulsion unit 14 and connected to an oil drain passage 62 reaching the gear housing chamber.

(1) Neutral mode (see FIGS. 3 (A) and 6 (B)) The stem valve 59 of the switching valve device 55 communicates the oil supply path 61 with either the forward oil path 64 or the reverse oil path 65. Instead, the forward oil passage 64 and the reverse oil passage 65 communicate with the oil drain passage 62 via the oil discharge passage 63. As a result, the forward hydraulic clutch 27
No high-pressure oil is supplied to the pressurizing chamber 29 of F and the pressurizing chamber 39 of the reverse hydraulic clutch 27R, the two hydraulic clutches 27F and 27R are in the clutch disengaged state, and the rotational force of the input shaft 16 is
5. The rotation is not transmitted to any of the reverse gears 26, and thus the rotation of the propeller 23 is stopped.

(2) Forward mode (see FIGS. 3 (B) and 6 (C)) The stem valve 59 of the switching valve device 55 communicates the oil supply path 61 with the forward oil path 64 and discharges the reverse oil path 65 with oil. It communicates with the oil drain passage 62 via the passage 63. As a result, high-pressure oil is supplied to the pressurizing chamber 29 of the forward hydraulic clutch 27F, the forward hydraulic clutch 27F enters the clutch connected state, and the input shaft 16
Is transmitted to the forward gear 25 and, consequently, the propeller 23
To rotate forward.

(3) Reverse mode (see FIG. 6 (A)) The stem valve 59 of the switching valve device 55 communicates the oil supply path 61 with the reverse oil path 65, and connects the forward oil path 64 with the oil drain via the oil discharge path 63. Communicates with Road 62. As a result, high-pressure oil is supplied to the pressurizing chamber 39 of the reverse hydraulic clutch 27R, the reverse hydraulic clutch 27R enters the clutch connected state, and the input shaft 16
Is transmitted to the reverse gear 26 and, consequently, the propeller 23
To reverse rotation.

The end face of the stem valve 59 is supported by a thrust bearing 59A.

However, in the switching valve device 55, as shown in FIGS. 4 to 6, two oil balance passages 101 and 102 branching from the oil supply passage 61 are formed in the stem valve 59 so that each oil balance is provided. The passages 101 and 102 are opened on the rear side of the outer peripheral portion of the stem valve 59 with respect to the position of the oil supply passage 61, and the radial force exerted on the stem valve 59 by the oil pressure in the oil supply passage 61 and the oil pressure Is set so that the radial force exerted on the stem valve 59 is balanced.

The oil balance passages 101 and 102 are separated from the oil supply passage 61 by 180 degrees in the circumferential direction with respect to the central axis of the stem valve 59, and have different axial positions.

However, in the embodiment of the present invention, a single oil balance passage 103 as shown in FIGS.
May be bored. The oil balance passage 103 is circumferentially spaced 180 degrees from the oil supply passage 61 with respect to the central axis of the stem valve 59, and has the same axial position.

Here, in each of the above-described modes, as shown in FIG. 4, the switching valve device 55 includes a neutral, forward, Or each concave part 68N, 68 of reverse
Engage with the F and 68R to maintain these modes.

A part of the oil pressurized by the oil pump 54 is branched from the upstream side of the switching valve device 55, and a front lubrication passage 69F and a rear lubrication passage extending to the drive unit housing 53 and the input shaft 16 are provided. Both hydraulic clutches 27F and 27R can be cooled and lubricated via 69R.

The input shaft 16 is a front bearing housing which is fitted and fixed in a liquid-tight manner to the front opening 51F of the propulsion unit 14 by bolts 70.
It is supported by a front bearing 72 incorporated in 71 and a rear bearing 73 incorporated in a drive housing 53 which also functions as a bearing housing fitted in the rear opening 51R. And each opening
The opening diameters of 51F and 51R are set larger than the outer diameters of the hydraulic clutch 27, the forward gear 25, and the reverse gear 26. Also, around the drive unit 50 on the upper rear surface of the propulsion unit 14, a cover is provided.
74 have been deposited.

The propeller shaft 19 is supported by a front bearing 75 having a front end incorporated in the propulsion unit 14, and has an intermediate bearing 77 and a rear bearing incorporated in a bearing housing 76 having an intermediate portion mounted on the propulsion unit 14. Supported at 78.

In addition, the intermediate shaft 20 is indirectly supported via an driven gear 24 on an upper bearing 79 having an upper end incorporated in the propulsion unit 14,
The intermediate portion is supported by an intermediate bearing 80 incorporated in the propulsion unit 14, and the lower end is supported by a lower bearing 81 incorporated in the propulsion unit 14.

 Next, the operation of the above embodiment will be described.

According to the above embodiment, the oil balance paths 101, 102 or
By selecting the opening position and opening area of 103, the oil supply path 6
The radial force exerted on the stem valve 59 by the oil pressure in 1 is set so that the radial force exerted on the stem valve 59 by the oil pressure in the oil balance path 101, 102 or 103 is balanced, thereby canceling both radial forces. Can be.
Therefore, in the switching valve device 55 of the hydraulic clutch 27 for the inboard / outboard motor 10, the rotational operation force of the stem valve 59 can be reduced by reducing the radial force acting on the stem valve 59, and the shift operation force can be reduced.

[Effects of the Invention] As described above, according to the present invention, in the switching valve device of the hydraulic clutch for a marine propulsion device, the radial force acting on the stem valve is reduced, thereby reducing the rotational operation force of the stem valve, and shifting. The operating force can be reduced.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an inboard / outboard motor to which the present invention is applied, FIG. 2 is a side view showing the appearance of the inboard / outboard motor, FIG.
(B) is a circuit diagram showing an operation circuit of the hydraulic clutch, FIG. 4 is a cross-sectional view showing a switching valve device, FIG. 5 is a cross-sectional view taken along the line VV in FIG. 4, and FIGS. (C) is VI-VI in FIG.
7 is a sectional view showing a switching state of the switching valve device in a line, FIG. 7 is a sectional view showing a modification of the present invention, and FIG.
FIG. 9 is a cross-sectional view taken along the line VIII, FIG. 9 is a cross-sectional view showing a conventional switching valve device, and FIGS. 10 (A) to 10 (C) show the switching state of the switching valve device along line XX in FIG. It is sectional drawing. 10 ... Inboard / outboard motor, 27, 27F, 27R ... Hydraulic clutch, 53 ... Housing, 55 ... Switching valve device, 58 ... Oil discharge passage, 59 ... Stem valve, 61 ... Oil supply passage, 64 …… Forward oil passage, 65 …… Reverse oil passage, 101, 102, 103 …… Oil balance passage.

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) B63H 23/30 F16D 25/11 F16K 11/085

Claims (1)

(57) [Claims] A stem valve is disposed in a housing, and the stem valve is rotatable around its own axis by an operating force applied to an operating portion of the stem valve. An oil supply passage extending to the outer peripheral surface of the oil distribution formed in the outer periphery of the stem valve is bored in the stem valve, and an oil discharge passage is opened in a portion of the housing facing the pressure receiving surface of the stem valve. In the part facing the oil distribution outer peripheral surface, a forward oil path communicating with the forward hydraulic clutch and a reverse oil path communicating with the reverse hydraulic clutch are opened, and the oil supply path is connected to the forward oil path by rotating a stem valve. The high-pressure oil supplied from the oil discharge path by selectively communicating with the reverse oil path is selectively divided into the forward hydraulic clutch and the reverse hydraulic clutch. In a switching valve device of a hydraulic clutch for a marine propulsion device, an oil balance passage branching from an oil supply passage is provided in a stem valve, and the oil balance passage is provided on a rear side of an oil supply passage opening position of an outer peripheral portion of the stem valve. A hydraulic clutch for a marine propulsion machine, wherein the hydraulic clutch for a marine propulsion device is set so that the radial force exerted on the stem valve by the oil pressure in the oil supply path and the radial force exerted on the stem valve by the oil pressure in the oil balance path are opened. Valve device.