JP5047348B2 - Steering machine - Google Patents

Description

  The present invention relates to a ram that is reciprocally driven by a fluid pressure cylinder such as a hydraulic cylinder, an engagement tool that can be engaged with the ram, and a reciprocating motion of the ram that is connected to the engagement tool and is converted into a rotational motion. The present invention relates to a marine steerer including a rotational drive mechanism that rotationally drives a rudder shaft.

FIG. 5 is a plan view of an essential part of a marine steerer disclosed in Patent Document 1 (Japanese Utility Model Publication No. 3-56479).
In FIG. 5, a rod-shaped ram shaft 1 is disposed on the same axis, and both ends of the ram shaft 1 are accommodated in hydraulic cylinders 6 and 6 supported by bearings 11 and 11 on the hulls 5 and 5. The ram shaft 1 is driven to reciprocate on the same axis by the hydraulic pressure of the hydraulic cylinders 6 and 6.
A ram pin 4 protrudes from the central large diameter portion of the ram shaft 1, and a three-dimensional bush 3 fitted and inserted in the axial direction of the ram pin 4 is inserted into the fork portion 26 of the fork-like chiller 2. The fork-like chiller 2 is fixed to a rudder shaft 7 of a ship with a key 8.

In such a marine steerer, when the hydraulic pressure is applied to one of the hydraulic cylinders 6 and 6 (for example, when the hydraulic pressure is applied to the right hydraulic cylinder 6), the ram shaft 1 moves as indicated by the X arrow, The movement is transmitted to the fork-like chiller 2 through the ram pin 4 and the three-dimensional bush 3, and the fork-like chiller 2 rotates as indicated by the arrow Y, so that the rudder shaft 7 fixed to the fork-like chiller 2 becomes Y Rotated as an arrow.
An anti-falling tool 8a is fixed to the three-dimensional bush 3, and the ram shaft 1 is prevented from rotating around its axis by guiding the anti-falling tool 8a along the horizontal guide rod 27. Yes.

Japanese Utility Model Publication No. 3-56479

FIG. 6 is a main part configuration diagram of the marine steering machine.
In such a steering machine, it is desirable that the mechanical efficiency of the device is high. However, in order to improve the mechanical efficiency, the frictional resistance that increases with the size of the rudder angle of the rudder shaft 7, between the bush 3 and the forked chiller 2 It is necessary to reduce the frictional resistance between the ram shaft 1 and the bush 3, the frictional resistance between the fall stopper 8a and the horizontal guide rod 27, and the like.
Of these frictional resistances, it is effective to reduce the frictional resistance that increases according to the rudder angle of the rudder shaft 7.

As shown in FIG. 6, the frictional resistance that increases according to the rudder angle of the rudder shaft 7 is such that the hydraulic load F of the hydraulic cylinder 6 (see FIG. 5) is, for example, from right to left as shown in FIG. , The load T associated with the ram shaft 1 and the bending load (component load) T ₁ in the vertical direction act on the axis 1a of the ram shaft 1 of the load T.
As shown in FIG. 6, the bending load T ₁ perpendicular to the axis 1 a increases as the movement amount S of the ram shaft 1 in the direction of the axis 1 a increases, that is, increases according to the rudder angle of the rudder shaft 7. To do.

Therefore, when said large steering angle of the steering shaft 7, the bending load _{T 1} is also increased, as the reaction force of the bending load _{T 1,} the reaction force _W 1 to the bearing 11, 11 of the hydraulic cylinder 6, _{W 2} The reaction forces W ₁ and W ₂ become the frictional resistance of the ram shaft 1.
Accordingly, although it is necessary to reduce the frictional resistance of the ram shaft 1 due to the reaction forces W ₁ and W ₂ , the above-described means of FIGS.

  In view of the problems of the prior art, the present invention provides a steering machine in which the frictional resistance of the ram shaft is reduced particularly when the steering angle of the steering shaft is large, and the mechanical efficiency of the entire steering machine is improved. Objective.

  The present invention achieves such an object, and a ram shaft that is reciprocally driven, an engagement tool that can be engaged with the ram shaft, and a reciprocating motion of the ram shaft that is connected to the engagement tool to rotate. In a steering machine having a rotation drive mechanism for rotating the rudder shaft by changing, the ram shaft is divided into a first ram shaft and a second ram shaft perpendicular to the axis, and the first ram shaft and the second ram shaft are divided. A contact surface comprising an involute curve in which a shaft end portion of the shaft dividing portion is formed in a curved shape, and the engaging tool abuts on the curved shaft end portion of the dividing portion of the first ram shaft and the second ram shaft. The engagement tool is fixed to the rudder shaft, and the rudder shaft is rotationally driven in conjunction with the contact surface made of the involute curve of the engagement tool. Claim 1).

  According to the present invention, the axial force from the drive source is always an axial load, and the axial force is separately handled by the first ram shaft and the second ram shaft. Therefore, there is no reaction force applied to the bearing due to the bending load perpendicular to the shaft, and there is no frictional resistance of the ram shaft due to such reaction force. In addition to the effect of improving the mechanical efficiency of the contact, since it is contact by an involute curve, if the shaft end portion of the divided portion is formed in an accurate curved surface shape, both of them will fall even if the fall increases. Since the contact surfaces are orthogonal, friction loss is reduced, and further improvement in mechanical efficiency is obtained.

Further, in the above invention, a cylindrical contact portion that is rotatably contacted with a shaft end portion of the divided portion of the first ram shaft and the second ram shaft, an outer ring of a rolling bearing, the first ram shaft and the second ram. Any of an abutting portion that abuts rotatably on the shaft end portion of the divided portion of the shaft, and a contact surface portion formed of an involute curve that abuts on the curved shaft end portions of the divided portions of the first ram shaft and the second ram shaft. If an oil supply device for supplying crab lubricating oil is provided (Claim 2),
Friction loss is reduced by supplying lubricating oil to the abutment portions on the first ram shaft side and the second ram shaft side by an oil supply device, and further improvement in mechanical efficiency is obtained.

According to the present invention, since the ram shaft is divided into the first ram shaft and the second ram shaft at right angles to the axis, the axial force from a drive source such as a hydraulic cylinder that reciprocates the ram shaft is applied to the first ram shaft. Each of the ram shaft and the second ram shaft acts separately, and the two shafts are rotatably contacted via a cylindrical body supported by the chiller. increases with increasing axial movement of the ram axis, perpendicular to the axis of the bending load (the component force load) T ₁ does not occur, the axial force from the driving source is always load in the axial direction, this Since the axial force is separately received by the first ram shaft and the second ram shaft, a bending load in the direction perpendicular to the shaft due to the axial force is not generated.

Therefore, there is no reaction force applied to the bearing due to a bending load perpendicular to the shaft, and there is no frictional resistance of the ram shaft due to the reaction force. The reduction in the frictional resistance can improve the mechanical efficiency of the entire steering machine.
Further, the first ram shaft and the second ram shaft are divided into two, the shaft end portions of the divided portions of the first ram shaft and the second ram shaft are formed in a curved shape, and the engagement tool is attached to the first ram shaft. Since the shaft and the second ram shaft are configured to have a contact surface made of an involute curve that abuts the curved shaft end of the divided portion of the second ram shaft, the rotation of the first ram shaft and the second ram shaft is not restricted. Therefore, unlike the conventional one, the means for moving the three-dimensional bush along the horizontal guide rod, that is, the horizontal guide rod and its supporting means are not required, and the structure is simplified.

  In the present invention, preferably, a reinforcing plate for connecting the first ram shaft and the second ram shaft so as not to be relatively movable is provided between a first ram shaft and a second ram shaft obtained by dividing the ram shaft. If provided (Claim 3), since the first ram shaft and the second ram shaft are connected by the reinforcing plate, the axial force from one side from the driving source, for example, from the first ram shaft side is the reinforcing member. Since it is transmitted directly from the other side through the plate to the second ram shaft, for example, the followability between the first ram shaft and the second ram shaft can be improved.

FIGS. 1A and 1B are main part configuration diagrams of a marine steering machine according to a first reference example of the present invention. FIG. 1A is a neutral configuration, and FIG. (Partial display is omitted). It is a principal part structure enlarged view of the steering gear for ships which shows the 2nd reference example of this invention. It is a principal part block diagram of the steering gear for ships which shows 3rd Example of this invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a principal part block diagram of the ship steering gear which shows 1st Example of this invention, (A) is the neutral state, (B) is a block diagram at the time of the action | operation of a hydraulic cylinder (Partial display of a hydraulic cylinder is shown. Is omitted). It is a principal part top view of the conventional marine steering machine. It is a principal part block diagram of the conventional ship steering gear.

  Hereinafter, the present invention will be described in detail with reference to embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this embodiment are not intended to limit the scope of the present invention only to the description unless otherwise specified. It is just an example.

[Reference Example 1]
FIGS. 1A and 1B are main part configuration diagrams of a marine steering machine according to a first reference example of the present invention. FIG. 1A is a neutral configuration, and FIG. (Partial display is omitted).
1A and 1B, a first ram shaft 1z and a second ram shaft are obtained by dividing a rod-shaped ram shaft arranged on the same axis in a stationary state into two equal parts perpendicular to the axis 1a of the ram shaft. It is divided into 1y. A cylindrical body 12 rotatably supported by the ram pin 4 is in contact with the shaft end faces 1s and 1s of the first ram shaft 1z and the second ram shaft 1y.
The ram pin 4 that rotatably supports the cylindrical body 12 has both ends of the ram pin 4 fixed to the fork-shaped chiller 2. Further, the fork-shaped chiller 2 is fixed to the rudder shaft 7 of the ship with a key 8. The rotation center of the rudder shaft 7 is indicated by 7a.

One end portion of the first ram shaft 1z is housed in the hydraulic cylinder 6, and one end portion of the second ram shaft 1y is housed in the hydraulic cylinder 6. The hydraulic pressures F and F applied to the hydraulic cylinders 6 and 6 The first ram shaft 1z, the second ram shaft 1y, and the cylindrical body 12 are driven so as to reciprocate on the axis of the hydraulic cylinder 6.
Bearings 11, 11 are fixed to the hydraulic cylinders 6, 6, and the first ram shaft 1 z and the second ram shaft 1 y are rotatably supported on the inner periphery of the bearings 11, 11.
Further, since the first ram shaft 1z and the second ram shaft 1y are cantilevered only by the bearings 11 and 11, the first ram shaft 1z and the second ram shaft 1y are supported by auxiliary bushes 13 and 13 inside the bearings 11 and 11, respectively. The second ram shaft 1y is supported.

In such a marine steering machine, as shown in FIG. 1B, when hydraulic pressure is applied to one of the hydraulic cylinders 6 and 6 (for example, when hydraulic pressure is applied to the right hydraulic cylinder 6), the first ram shaft 1z moves in the M arrow direction, and the cylindrical body 12 and the second ram shaft 1y move in the M arrow direction following this.
Movement of such cylinder 12 is transmitted to the chiller 2 forked through the Ramupin 4, the chiller 2 is rotated as Y ₁ arrow, steering shaft 7 which is fixed to the chiller 2 is the rotational center 7a It is rotated as Y ₁ arrow around.

According to the first reference example, the ram shaft is equally divided into two at right angles to the axis 1a to be divided into the first ram shaft 1z and the second ram shaft 1y, and the first ram shaft 1z and the second ram shaft 1y. The cylindrical body 12 is configured to be rotatably contacted with the shaft end portions 1 s and 1 s of the divided portion. The cylindrical body 12 is rotatably supported by the ram pin 4, and both ends of the ram pin 4 are attached to the fork-shaped chiller 2. The chiller 2 is fixed to the rudder shaft 7 of the ship with a key 8.
Therefore, according to the first reference example, by dividing the ram shaft into the first ram shaft 1z and the second ram shaft 1y, the axial force F from the hydraulic cylinders 6 and 6 that reciprocally drive the ram shaft is obtained. The first ram shaft 1z and the second ram shaft 1y act separately, and the two shafts are in contact with each other through the cylindrical body 12 supported by the chiller 2, so that the conventional ram shaft is such as those integrated (as shown in FIG. 6), the bending load (the component force load) T ₁ in the direction perpendicular to the axis of increasing with increasing axial movement of the ram shaft is not generated, the hydraulic cylinder 6, The axial force F from 6 is always a load only in the axial direction 1a. Since this axial force F is separately handled by the first ram shaft 1z and the second ram shaft 1y, the axial force F is applied to the axis by the axial force F. bending load T ₁ of the vertical direction does not occur.

Accordingly, there is no generation of reaction forces W ₁ and W ₂ applied to the bearing due to the bending load T ₁ perpendicular to the shaft (see FIG. 6), and there is no frictional resistance of the ram shaft due to the reaction forces W ₁ and W ₂ . By reducing the frictional resistance, the mechanical efficiency of the entire steering machine can be improved.
Further, the first ram shaft 1z and the second ram shaft 1y are divided into the two ram shafts 1z and 1y so that the two ram shafts 1z and 1y are rotatably in contact with each other via the cylindrical body 12. The rotation of the shaft 1y is not constrained. Therefore, as in the prior art (see FIG. 6), means for moving the fall stop 8a along the horizontal guide rod 27, that is, the horizontal guide rod 27 and its supporting means. Is unnecessary, and the structure is simplified.

[Reference Example 2]
FIG. 2 is an enlarged view of a main part configuration of a marine steering machine according to a second reference example of the present invention.
As in the first reference example, the second reference example divides a rod-shaped ram shaft arranged on the same axis line in a stationary state into two equal parts perpendicular to the axis line 1a of the ram shaft. And the second ram shaft 1y.
The outer ring 14 is rotatably abutted on the shaft end portions 1s, 1s of the divided portion of the first ram shaft 1z and the second ram shaft 1y, and the rotation of the outer ring 14 is caused by rolling elements (a plurality of spherical bodies or roller bodies). ) 15 and a rolling bearing 14a connected to the inner ring 12a is provided, and the inner ring 12a of the rolling bearing 14a is rotatably supported by the ram pin 4.
Both ends of the ram pin 4 are fixed to a fork-shaped chiller 2, and the fork-shaped chiller 2 is fixed to a rudder shaft 7 of a ship with a key 8 as in the first reference example.

According to the second reference example, the ram shaft is divided into the first ram shaft 1z and the second ram shaft 1y, and the outer ring 14 is the axis of the divided portion of the first ram shaft 1z and the second ram shaft 1y. A rolling bearing 14a is provided which is rotatably contacted with the end portions 1s and 1s and connects the rotation of the outer ring 14 to the inner ring 12a via a rolling element (a plurality of spheres or rollers) 15, and the inner ring 12a of the rolling bearing 14a is provided. Since the ram pin 4 is rotatably supported by the ram pin 4, the ram shaft is equally divided into two at right angles to the axis and divided into the first ram shaft 1z and the second ram shaft 1y. 14, a rolling bearing 14a composed of a rolling element (a plurality of spheres or rollers) 15 and an inner ring 12a is supported by the chiller 2 so that the outer ring 14 of the rolling bearing 14a can be freely rotated around the shaft end portions 1s and 1s of the divided portion. By contact, it can be kept when hydraulic pressure F is activated. , The frictional resistance due to contact of the outer ring 14 of the rolling bearing 14a and the first ram shaft 1z and second ram shaft 1y is further reduced, thereby further increasing the effect of improving the mechanical efficiency of the overall steering gear.
Other configurations are the same as those of the first reference example, and the same members are denoted by the same reference numerals.

[Example 3]
FIG. 3 is a block diagram showing a main part of a marine steering machine according to a third embodiment of the present invention.
In the third embodiment, like the first reference example and the first embodiment described later, a rod-shaped ram shaft arranged on the same axis in a stationary state is divided into two equal parts perpendicular to the axis 1a of the ram shaft. Thus, the first ram shaft 1z and the second ram shaft 1y are divided.
In the third embodiment, the first ram shaft 1z and the second ram shaft 1y are relatively moved between the first ram shaft 1z and the second ram shaft 1y obtained by dividing the ram shaft into two equal parts. The reinforcing plate 16 that is impossiblely connected is fixed by welding (it may be bolted).
Further, in the third embodiment, there is provided an anti-falling device 8a fixed to the first ram shaft 1z and the second ram shaft 1y, and the anti-falling device 8a is guided along the horizontal guide rod 28. Thus, the first ram shaft 1z and the second ram shaft 1y are prevented from rotating around the axis 1a.

According to the third embodiment, since the first ram shaft 1z and the second ram shaft 1y are connected by the reinforcing plate 16, for example, the first ram from one side from the hydraulic cylinders 6 and 6 (see FIG. 1). Since the axial force F from the shaft 1z side is directly transmitted to the second ram shaft 1y side through the reinforcing plate 16, the followability between the first ram shaft 1z and the second ram shaft 1y is improved. be able to.
Other configurations are the same as those of the first embodiment, and the same members are denoted by the same reference numerals.

[Example 1]
4A and 4B are main part configuration diagrams of a marine steering machine according to a first embodiment of the present invention, in which FIG. 4A is a neutral configuration, and FIG. 4B is a configuration diagram of a hydraulic cylinder (one hydraulic cylinder). (Partial display is omitted).
In the first embodiment, as in the third embodiment, a rod-shaped ram shaft arranged on the same axis in a stationary state is equally divided into two at right angles to the axis 1a of the ram shaft. 1z and the second ram shaft 1y.
The shaft ends of the divided portions of the first ram shaft 1z and the second ram shaft 1y are formed as spherical curved surface portions 1c, 1d, and the curved surfaces of the divided portions of the first ram shaft 1z and the second ram shaft 1y. The surface of the chiller that comes into contact with the surfaces of the ridges 1c and 1d is formed in an arc-shaped chiller 20 that is configured as a contact surface 20a that is an involute curve. The arc-shaped chiller 20 is fixed to the rudder shaft 7.

  As shown in FIG. 4B, when the hydraulic pressure F is applied to one of the hydraulic cylinders 6 and 6 (see FIG. 1) (for example, when the hydraulic pressure is applied to the right hydraulic cylinder 6), the first ram shaft 1z. The curved surface portion 1c comes into contact with the contact surface 20a of the arc-shaped chiller 20 having an involute curve, and the contact surface 20a and the second ram shaft 1y move in the direction of the arrow V and are fixed to the arc-shaped chiller 20. The rudder shaft 7 is rotated around the rotation center 7a in the direction of the arrow V.

According to the first embodiment, the axial force F from the hydraulic cylinders 6 and 6 is always a load in the axial direction 1a, and the axial force F is separately applied to the first ram shaft 1z and the second ram shaft 1y. Therefore, the bending load T ₁ (see FIG. 6) perpendicular to the shaft due to the axial force F does not occur, and therefore the reaction forces W ₁ and W ₂ (W ₂ (W) applied to the bearing due to the bending load T ₁ perpendicular to the shaft). 6), the frictional resistance between the first ram shaft 1z and the second ram shaft 1y due to the reaction forces W ₁ and W ₂ is eliminated, and the mechanical efficiency of the entire steering gear is improved by reducing the frictional resistance. The effect that it can be made is acquired.

  In addition, since the contact is made by the involute curve of the arc-shaped chiller 20, if the curved surface portions 1c and 1d of the divided portion are formed in an accurate curved surface shape, both contact surfaces 20a are orthogonal to each other even if the fall is increased. Friction loss is reduced, and further improvement in mechanical efficiency is obtained.

[Example 2]
In the second embodiment, an automatic oil supply device 24 for supplying lubricating oil is provided in FIG. 1, and the automatic oil supply device 24 makes contact between the cylindrical body 12, the first ram shaft 1z, and the second ram shaft 1y. Lubricating oil is supplied to
In addition to the above, the abutment that rotatably contacts the outer ring 14 of the rolling bearing 14a and the shaft end 1s of the divided portion of the first ram shaft 1z and the second ram shaft 1y in FIG. 2 (reference example 2). , And an arcuate chiller comprising an involute curve that abuts the curved shaft end of the divided portion of the first ram shaft 1z and the second ram shaft 1y in FIGS. 4A and 4B (Example 1). An automatic oiling device 24 that supplies lubricating oil to any one of the 20 contact surfaces 20a is provided.
According to the second embodiment, the lubricating oil is supplied to the abutment portions on the first ram shaft 1z side and the second ram shaft 1y side by the automatic oil supply device 24, whereby the friction loss is reduced and the mechanical efficiency is reduced. Further improvement is obtained.

  ADVANTAGE OF THE INVENTION According to this invention, the friction resistance of a ram axis | shaft can be reduced especially when the rudder angle of a rudder axis | shaft is large, and the steering machine which improved the mechanical efficiency of the whole steering machine can be provided.

1z 1st ram shaft 1y 2nd ram shaft 1c, 1d Curved surface portion 1s Shaft end surface 2 Chiller 4 Ram pin 6 Hydraulic cylinder 7 Rudder shaft 7a Rotation center 11 Bearing 12 Cylindrical body 12a Inner ring 13 Auxiliary bush 14 Outer ring 14a Rolling bearing 15 Rolling body (Sphere or roller)
16 Reinforcement plate 20 Arc-shaped chiller 20a Contact surface (involute curve)
24 Automatic refueling device F Hydraulic pressure

Claims (3)

A reciprocating ram shaft, an engagement tool engageable with the ram shaft, and a rotation drive mechanism connected to the engagement tool for rotating the rudder shaft into a rotational motion to rotate the rudder shaft. In the steering machine with
The ram shaft is divided into a first ram shaft and a second ram shaft at right angles to an axis line, and shaft end portions of the divided portions of the first ram shaft and the second ram shaft are formed in a curved surface, and the engagement tool Is formed on a contact surface made of an involute curve that contacts the curved shaft end portion of the divided portion of the first ram shaft and the second ram shaft, and the engagement tool is fixed to the rudder shaft, A steerer configured to rotate the rudder shaft in conjunction with a contact surface formed of the involute curve of the combination.   A cylindrical abutting portion that is rotatably abutted against an axial end portion of the split portion of the first ram shaft and the second ram shaft; an outer ring of a rolling bearing; and a split portion of the first ram shaft and the second ram shaft. Lubricating oil is applied to any one of an abutting portion that abuts rotatably on the shaft end portion, and a contact surface portion formed of an involute curve that abuts the curved shaft end portion of the divided portion of the first ram shaft and the second ram shaft. The steering machine according to claim 1, further comprising an oil supply device to be supplied.   The reinforcing plate for connecting the first ram shaft and the second ram shaft so as not to move relative to each other is provided between a first ram shaft and a second ram shaft obtained by dividing the ram shaft. The steering machine according to 1 or 2.

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