JPS62242136A - Reverse and reduction gear for ship - Google Patents

Abstract

PURPOSE:To relieve the shock at the time of the start, by providing a portion of plural clutch units, which are given a fitting or detaching motion by an oil pressure working part, with another oil pressure working part, which starts its motion with the pressure lower than that for the other clutch units. CONSTITUTION:A cylinder 19 is formed at a part of an advancing force input gear of an advancing force supporting shaft 12a, while an operating oil pressure chamber 24 is formed between the cylinder 19 and a piston body 20 that is pushed by a return spring 22. In addition, a wall surface of the piston body 20 is indented in order to form an initial, pressure receiving chamber 25a. Thus, the greater the pressure receiving area is, the lower the oil pressure, at which the piston starts its motion, becomes, and the piston pushes a multiple disc clutch part 34, thereby realizing a clutch-fit-in state. In this connection, another advancing force supporting shaft is formed in the same way as the said shaft 12 except that the pressure receiving area of the initial, pressure receiving chamber is made smaller than the above case. Accordingly, both advancing force supporting chambers cooperate with each other in putting on or off the power between the input shaft and the output shaft, thereby shortening the clutch-fit-in time and also relieving the shock.

Description

[Detailed description of the invention] Industrial applications The present invention relates to a marine speed reduction/reversal gear.

Conventional technology In general, a marine reduction/reversing gear is provided with support shafts for forward movement and reverse movement in the case of the reduction/reversal gear, and each support shaft is equipped with a hydraulic actuator that is supplied with hydraulic oil from an oil pump or the like. , a clutch unit consisting of a clutch and a clutch part operated by the hydraulically operated part is provided, and when moving forward, hydraulic oil is supplied to the hydraulically operated part on the forward support shaft,
This connects the clutch section, while supplying hydraulic oil to the hydraulic operating section on the reverse support shaft during reversing.
The clutch section is connected in the same manner.

By the way, this type of marine speed reduction/reversing gear has multiple support shafts for forward or reverse movement in parallel, in addition to the one-axis forward/reverse type in which each support shaft is one for forward and one for reverse. There is one that aims to have multiple shafts by installing a clutch unit and operating the clutch units provided in each of them in cooperation with each other. Examples of such devices include, for example, two forward axes and one reverse axle type, two forward axes and two reverse axes, and other multi-axis forward and reverse axes types.

Conventionally, for example, the clutch unit for forward movement in a 2 forward axle and 1 reverse axle type, or the clutch unit for forward and reverse in a 2 forward axle and 2 reverse axle type, or a multi-shaft forward/reverse type, has the same structure. It was designed to have a high-performance hydraulic operating section.

Problems to be Solved by the Invention However, in this type of marine reduction/reversing gear, hydraulic oil supplied from a hydraulic source such as an oil pump is switched between forward, reverse, and neutral states using a switching valve. ing. In this case, in the case where the clutch units are arranged in parallel, it is necessary to commonly supply hydraulic oil to both hydraulic actuating parts. On the other hand, in order to start the operation of the hydraulic actuation section, it is necessary to generate a force for moving the piston body against the biasing force of the return spring, frictional resistance, etc., using the hydraulic pressure acting on the piston body.

Therefore, in a conventional clutch unit in which each clutch unit has a hydraulic actuator with the same performance, the clutch engagement time from switching the switching valve until the output shaft starts rotating is longer than in the case of a single-shaft type. In that case, since both clutch units are connected almost simultaneously, there is a problem in that the impact of engagement is large (and causes discomfort to the passenger).In addition, if only to alleviate the impact of engagement, it is necessary to use the hydraulically actuated It is also conceivable to install a slow-fitting valve in the hydraulic circuit to the clutch, but if this is done, there is a problem that it takes more time for the oil pressure to rise and the clutch fitting time becomes even longer.

In view of these problems, the present invention provides a system in which a plurality of clutch units on separate shafts share hydraulic pressure to their hydraulic actuating parts and cooperate to engage and disengage power. This was done with the aim of alleviating the clutch engagement shock caused by the clutch unit and shortening the clutch engagement time.

Means for Solving the Problems Technical means for achieving the above object will be explained using FIGS. 1 to 4 showing an embodiment of the present invention. That is,
In the present invention, each of the support shafts (12a) (1
2b) supported by the shilling body (19) (1
9), and hydraulic actuating parts (18a) (18b) equipped with piston bodies (20) (20) slidably inserted into the cylinder bodies (19) (19), and also the support It includes clutch parts (34) (34) supported on the shafts (12a) (12b) and engaged and disengaged by the hydraulic actuation parts (18a) (18b), and the hydraulic actuation parts (18a) (18b). In a device having a plurality of clutch units 71 (13a) (13b) that share a working hydraulic pressure and cooperate to engage and disengage power, some clutch units of the plurality of clutch units (13a) (13b). (13a) is provided with a hydraulically actuating part (18a) that starts operating at a lower hydraulic pressure than the hydraulically actuating part (18b) of the other clutch unit (13b).

Operation By having the above configuration, after switching the clutch,
As hydraulic oil pressure increases, multiple clutch units (1
3a) (13b) One of the clutch units (
Only the hydraulic operating section 13a)<18a) starts operating,
The clutch engagement operation will be performed quickly. Then, when the working oil pressure increases further, the hydraulic actuating portion (18b) of the remaining clutch unit (13b) starts operating.

EXAMPLES Below, an example will be described in which the present invention is applied to a 2 forward axle and 2 reverse axle type marine speed reduction/reversal machine.

In Fig. 2, (1) shows the case (hereinafter simply referred to as the "case") of the speed reduction/reversing machine, and this case (1)
An input shaft (2) is disposed horizontally in the first half, and an output shaft (3) is disposed horizontally in the second half.

One of the input shafts (2) is rotatably supported at both ends thereof via bearings (4) and (5) approximately in the vertically intermediate portion of the case (1), and its front end side is (
1) and protrudes forward. (6) shows an input gear provided integrally with the input shaft (2) within the case (1). Further, (7) shows an input shaft joint attached to the front end portion of the input shaft (2). The other output shaft (3) penetrates a bearing box (8) provided on the rear side of the case (1) below the input shaft (2) in the case (1) and projects rearward. At the same time, it is rotatably supported via bearings (9) (9) installed in the bearing box (8). Further, the front end side of the output shaft (3) is supported via a bearing (11) provided on the intermediate support wall (10) within the case (1). (
12) shows an output shaft joint externally fitted and fixed to the rear protruding end of the output shaft (3).

Above these input shafts (2) and output shafts (3), as shown in Fig. 3, forward support shafts (
Forward clutch units (13a) and (13b) supported by 12a and 12b are disposed on both left and right sides.

First, the left forward clutch unit I-(
13a) will be explained. Forward support shaft (12a)
has a first one on the front end side in the case (1).
As shown in the figure, the boss portion (14) of the forward input gear (14)
a) is externally fitted and fixed. (15) is this boss part (
14a) shows a bearing interposed between the front wall of the case (1) on the front end side, and (16) shows the bearing interposed between the case (1) and the front wall of the forward support shaft (12a); (1) Shows a bearing interposed between the rear wall and the rear wall. With these bearings (15) (16),
The forward support shaft (12a) is rotatably supported by the case (1).

A cylindrical clutch housing (17) is provided on the rear side of the boss portion (14a) of the forward input gear (14), and a cylindrical clutch housing (17) is provided on the front side of the clutch housing (17). A cylinder (19) constituting a part of the hydraulic operating part (18a) of the forward clutch unit (13a) is formed continuously on the inner wall surface of the boss part (14a).

That is, in this embodiment, the forward input gear (14)
The boss portion (14°a) is a part of the cylinder body.

A piston body (20) is inserted into the cylinder (19) so as to be slidable in the front-rear direction. The piston body (20) has an inner cylindrical portion (21) that protrudes rearward while being in sliding contact with the forward support shaft (12a), and a spring receiver (22) that is also fixed on the forward support shaft (123).
) is interposed between the forward support shaft (12a) and a coil spring-like return spring (23), which moves the piston body (20) forward. It is energizing. The piston body (20) also has an initial pressure receiving chamber (25a) which is recessed on the wall surface facing the hydraulic pressure chamber (24) formed between the piston body (20) and the cylinder (19). ) is formed. on the other hand,
A hydraulic oil passage (26) is formed inside the forward support shaft (12a) along its longitudinal direction, and a hydraulic oil port (27) provided at one end of the hydraulic oil passage (26)
It opens facing the aforementioned hydraulic pressure chamber (24). Hydraulic oil is supplied to the hydraulic oil passage (26) via a switching valve (not shown). Note that when no hydraulic oil is supplied to the hydraulic pressure chamber (24), , the piston body (20) is pushed by a return spring (23) acting on the inner cylinder part (21) and hits the inner wall surface of the boss part (14a) except for the initial pressure receiving chamber (25a) in the central part. Therefore, in the initial state when the switching valve is opened and the supply of hydraulic oil to the hydraulic oil passage (26) is started, the initial pressure receiving chamber (25a ) Hydraulic oil flows in. Note that the force that moves the piston body (20) in the axial direction is due to the hydraulic pressure acting on the piston body (20) in the hydraulic pressure chamber (24). ) forward support shaft (12a)
It is the size multiplied by the area perpendicular to . Therefore, the forward support shaft (12a) of the initial pressure receiving chamber (25a)
The larger the area perpendicular to the piston body (20), the easier it is for the piston body (20) to move against the return spring (23), in other words, the hydraulic actuating part (18a) starts operating at a lower oil pressure. .

On the other hand, a forward pinion (28) is supported in an idling state on the rear end side of the forward support shaft (12a) in the case (1). A cylindrical protruding end (29) formed by extending the boss portion of the forward small gear (28) forward is inserted into the clutch housing (17). Between the protruding end (29) and the clutch housing (17), there are a number of drive plates (30) (30)... and driven plates (31) (31). ...are arranged alternately. One drive plate (30) (30)...
... engages with the spline portion (32) on the inner circumference of the clutch housing (17), and the other driven plate (31)
(31) are engaged with the spline portion (33) on the outer periphery of the protruding end portion (29), and these constitute a multi-disc clutch portion (34). In front of this multi-plate clutch section (34), the piston body (2
0), an outer cylindrical portion (35) that protrudes rearward while being in sliding contact with the inner circumferential wall of the cylinder (19) is disposed. Further, at the rear of the multi-plate clutch section (34), an annular pressure receiving member (
36) is located. That is, by supplying hydraulic oil to the hydraulic operating section (18a) via the hydraulic oil passage (26), the piston body (20) returns to the spring (23).
), the driving plates (30) (30) and 30 move backward against the force of
. . . and the driven plate (31) <31) are brought into pressure contact with each other, resulting in a clutch fitted state.

Further, the forward input gear (14) fixed to the forward support shaft (12a) is constantly meshed with the input gear (6) of the input shaft (2), and the forward input gear (14) is also fixed to the forward support shaft (12a).
) is freely rotatably supported by the forward pinion (28), which is connected to the output shaft (3
) is constantly meshed with the output large gear (37) which is externally fitted and fixed.

On the other hand, the right forward support shaft (12b) in FIG.
Also, the boss portion (14b) of the forward input gear (14) is externally fitted and fixed, and even in this case, the forward input gear (14) is always meshed with the input gear (6) of the input shaft (2). are doing. Further, the forward small gear (28), which is also freely supported by the forward support shaft (12b), is connected to the output large gear (37).
) are always engaged.

In the forward clutch unit 7 (13b) supported by this forward support shaft (12b),
As shown in FIG. 4, it is almost the same as the left forward thalassometry (13a) described above, except for a part of the hydraulic operating part (18b). That is, even in this case, the forward input gear (14) fixed to the forward support shaft (12a)
) is integrated with the boss part (14b) of the clutch housing (
17), a cylinder (19) is formed in the clutch housing (17), and a piston body (20) having the same shape as above is attached to the cylinder (19).
) is interpolated as slidable. In addition, the return spring (2
3) is also common in that the piston body (20) is urged to return to its initial state. However, this case is different in the shape of the initial pressure receiving chamber (25b), which has a recessed wall portion facing the hydraulic pressure chamber (24) of the piston body (20). That is, this piston body (20
) The initial pressure receiving chamber (25b) is designed to have a smaller initial pressure receiving area than that shown in FIG. Also, in this case, the forward support shaft (12b)
A hydraulic oil port (27) of the hydraulic oil passage (26), which is provided through the hydraulic oil passage (26) in the axial direction, is opened facing the hydraulic pressure chamber (24), and hydraulic oil is supplied through the hydraulic oil port (27). It is designed to supply

In addition, hydraulic oil is supplied to the hydraulic oil passage (26) in parallel with the hydraulic oil passage (26) from a switching valve that supplies hydraulic oil to the hydraulic oil passage (26) shown in FIG. It is supposed to be done. Therefore, by operating the aforementioned switching valve, the re-advance Taranochi unit (13a) (1
3b) works together to transmit power between the input and output shafts (2) and (3).

Next, regarding the clutch engagement operation during forward movement, the fifth
This will be explained with reference to FIGS.

First, in the first state when the switching valve is switched from the neutral position to the forward position, that is, in the initial state, as shown in FIG.
As shown in B), both hydraulic actuators (18a) (18
The piston bodies (20) (20) of b) are each pressed by a return spring (23) (23), and the initial pressure receiving chambers (25) of both piston bodies (20) (20)
a) Hydraulic oil flows only into (25b) via the hydraulic oil port (27) (27). In this state, both forward clutch units (13a) (13a)
are in a disconnected state. When both the initial pressure receiving chambers (25a) (25b) are filled with hydraulic oil and the hydraulic oil pressure increases, as shown in FIG. 6(B), the initial pressure receiving chamber (25a) with a large initial pressure receiving area
) The piston body (20) of the hydraulic operating part (18a)
begins to move against the return spring (23), and the forward clutch unit (13a) having its piston body (2o)
Only then will it begin to intrude. In such a situation,
The force exerted by the hydraulic oil pressure on the piston body (20) with a smaller initial pressure-receiving area is smaller than the biasing force of the return spring (23), and therefore, as shown in FIG. (13a) does not reach the start of insertion. Then, the piston body that started moving first (
20) receives a reaction force from the multi-disc clutch part (34) that comes into contact with its outer cylinder part (35), and when the hydraulic oil pressure starts to gradually increase, the other piston body (20)
It also begins to move against the return spring (23), and eventually the figure 7 (
A) Both forward clutch units (
13a) and (13b) are completely inserted.

FIG. 8 is a graph comparing the clutch characteristics obtained from the experimental results of this example with the clutch characteristics of the same type of conventional clutch, in which the horizontal axis shows the elapsed time after switching, and the vertical axis The hydraulic pressure and the output shaft rotation speed are taken into account. That is, in the figure, the time course of the hydraulic oil pressure in this embodiment is shown by a broken line, and the time course of the output shaft rotational speed is shown by a solid line. On the other hand, the one-dot chain line indicates the hydraulic oil pressure in the conventional example, and the two-dot chain line indicates the output shaft rotation speed. As is clear from comparing the two, the fitting time in this example is shorter than in the conventional case. Only one piston body (20) has moved up to the peak of the hydraulic pressure curve, and the other piston body (20) begins to move at that peak. Therefore, there is a time lag in the start of fitting of both piston bodies (20) (20), and the fitting shock is alleviated.

In addition, these double forward clutch units (13a') (
13b), around the input shaft (2) and output shaft (3), as shown in FIG.
Reverse support shafts (38a) (38b) are arranged, and the reverse support shafts (38a) (38b)
Reverse clutch unit (39a) having substantially the same structure as the forward clutch units (13a) and (13b) described above.
(39b) is supported. In this case as well, the hydraulic operating section of one reverse clutch unit (39a) has a configuration substantially similar to that shown in FIG. 1, and the hydraulic operating section of the other reverse clutch unit (39b) is shown in FIG. 4. It has almost the same configuration as the original.

Then, those reverse support shafts (38a) (38b
) includes reverse input gears (40) (40) that are always meshed with the forward input gears (14) (14), and reverse small gears (41) that are also constantly meshed with the large output gear (37).
) (41).

Therefore, even when moving backward, the insertion time is shortened and the insertion shock is alleviated, as in the case of forward movement.

Next, FIGS. 9 and 10 show another embodiment of the present invention. In this example, both cylinders (5 cylinders (1
9) Piston body (20) inserted into (19) (20
) have the same shape, while cylinders (19) (19
The shape of the > side has been changed. That is, one cylinder (19) has an operating hydraulic chamber (24) as shown in FIG.
) is slightly wider and recessed to form an initial pressure receiving chamber (25c) with a relatively large cross-sectional area. An initial pressure receiving chamber (25d) with a small cross-sectional area is formed.

Therefore, even in this case, both hydraulic oil passages (
26) By supplying hydraulic oil through (26), one of the hydraulic actuating parts (18a) having the initial pressure receiving chamber (25c) with a large initial pressure receiving area starts operating first, and the one with the small initial pressure receiving area The other hydraulic operating section (18b) having the initial pressure receiving chamber (25d) starts operating a little later.

In addition, while the shapes of the piston body and cylinder body in both hydraulic actuating parts are the same as shown in Fig. 1, for example, the return springs that bias both piston bodies are used with different spring constants. Alternatively, the biasing force of both piston bodies may be changed by incorporating a shim or the like into the return spring. Then, because the biasing force of the return spring is smaller on one piston body than on the other piston body, that one piston body starts moving first and enters the clutch engagement state, and the other piston body also acts on it. When the force of the hydraulic pressure overcomes the biasing force of the return spring, the movement begins, and the fully inserted state is achieved.

In addition, although the present invention has been explained only in the case of a 2 forward axle and 2 reverse axle type, even in a 2 forward axle and 1 reverse axle type, there are almost no changes to the two clutch units 7 on the forward side. It is possible to carry out the necessary tasks. It can also be easily applied to forward/reverse multi-axis types. In that case, the hydraulically actuating section in one of the plurality of clutch units is started to operate at a lower hydraulic pressure than the hydraulically actuating section in the other clutch units.

Effects of the Invention As described above, the present invention provides that each clutch unit includes a hydraulic actuating section that includes a cylinder body supported by a support shaft and a piston body movably inserted into the cylinder body. and also supported on the support shaft,
a clutch part that is engaged and disengaged by the hydraulic actuating part, and a common hydraulic pressure acting on the hydraulic actuating part;
In a device that has a plurality of clutch units that work together to engage and disengage power, some of the clutch units have a hydraulic actuator that starts operating at a lower hydraulic pressure than the hydraulic actuator of the clutch unit 6. Therefore, after the clutch is switched, only the part of the hydraulic actuating part receives the hydraulic oil pressure and starts operating, and the clutch having the hydraulic actuating part starts operating. Only the unit is in the clutch engaged state,
The effect of shortening the fitting time can be obtained. Moreover, since the front clutch units do not fit in at the same time, there is an advantage that the shock of fitting in is alleviated.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of one forward clutch unit in an embodiment of the present invention, FIG. 2 is a cross-sectional view of a two-forward axle reverse two-shaft reduction/reversal machine in which the present invention is implemented, and FIG. Similarly, FIG. 4, a schematic diagram showing the arrangement of gears, is the same (a cross-sectional view of the main part of the hydraulic actuating part of the other forward clutch unit, FIG. 5).
Figures (A) and (B) to Figures 7 (A) and (B) are operation explanatory diagrams showing the operating states of the hydraulic actuating parts in both forward clutch units, and Figure 8 is the same as Figures 1 and 4. 9 and 10, which are graphs showing experimental results according to the illustrated embodiment, are sectional views of essential parts showing the vicinity of the hydraulically actuated parts of both forward clutch units in another embodiment of the present invention. (12a) (12b) --- Forward support shaft, (13a
) (13b)...Forward clutch unit, (18a)
(18b)-=hydraulic actuating part, (19)... cylinder,
(20)... Piston body, (23)... Return spring,
(24)...Operating hydraulic chamber, (25a) (25b) (2
5c) (25d) = initial pressure receiving chamber, (34)... multi-plate clutch section.

Claims (1)

[Scope of Claims] 1. Each of them has a hydraulic actuator including a cylinder body supported by a support shaft and a piston body etc. slidably inserted into the cylinder body, and also the support A clutch unit that is supported on a shaft and is engaged and disengaged by the hydraulic actuating part, and has a plurality of clutch units that share the hydraulic pressure acting on the hydraulic actuating part and cooperate to engage and disengage the power. A marine speed reduction/reversing machine, wherein some of the plurality of clutch units are provided with a hydraulic actuation section that starts operating at a lower hydraulic pressure than the hydraulic actuation sections of other clutch units. 2. An initial pressure receiving chamber having a larger initial pressure receiving area than that of the piston bodies of other hydraulic operating parts is provided on the side of the piston body in the hydraulic operating part facing the working hydraulic chamber between the piston body and the cylinder body. 2. A marine speed reduction/reversing machine according to claim 1, wherein the hydraulically operated section starts operating at a lower hydraulic pressure than the other hydraulically operated sections. 3. An initial pressure receiving chamber with a larger initial pressure receiving area than that of the cylinder bodies of other hydraulic operating parts is provided on the side of the cylinder body in the hydraulic operating part facing the working hydraulic chamber between the cylinder body and the piston body. 2. A marine speed reduction/reversing machine according to claim 1, wherein the hydraulically operated section starts operating at a lower hydraulic pressure than the other hydraulically operated sections. 4. By making the biasing force of the return spring that biases the piston body in the hydraulically actuated part smaller than that of other hydraulically actuated parts, that hydraulically actuated part starts operating at a lower oil pressure than other hydraulically actuated parts. A marine speed reduction/reversing machine according to claim 1, wherein