JPS62113943A - Forward-rearward two speed type reduction reversing device for ship - Google Patents

Abstract

PURPOSE:To realize a specification of two shafts for two machines, by engaging a driven gear coaxially arranged on an output shaft with forward and rearward driving gears, and disposing an engagement-disengagement operation part for first and second speed and two series of planetary gears having a different number of teeth from each other, around the output shaft. CONSTITUTION:A small gear 15 capable of fixing, to a forward shaft 11, a clutch housing 13 for constructing a forward unit 12 provided with a forward input gear 14, by means of a forward clutch 18, is loosely fitted around the forward shaft 11. On the other hand, a large gear 23 serving as a driven gear which is engaged with the small gear 15 is loosely fitted around an output shaft 18 and a coupled planetary gear 29 having big and small teeth 29a, 29b, respective number of which are different from each other, is disposed on the carrier 23. Further, a first speed clutch 35, a second speed brake 36 for and an internal gear 29 are disposed. A rearward unit having the similar structure to that of the forward unit 12 is disposed on the side of the forward unit 12 and the output unit 18. Accordingly, the forward and rearward power transmitted to the large gear 23 are transmitted to the output shaft 18 in the different number of revolution, thereby realizing a specification of two shafts for two machines.

Description

[Detailed description of the invention] Industrial applications BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a marine speed reduction/reversal gear.

Conventional technology Conventionally, this type of marine speed reduction/reversing gear has been developed, for example, by the
- 2 forward speeds and 1 reverse speed as described in Publication No. 54754
There is a quick version.

As shown in Fig. 8, a forward drive unit (2), a reverse drive unit (3), and a forward two-speed unit (4), each equipped with a clutch mechanism, are installed in the reduction/reversal gear case (1). A forward drive gear (6) arranged around the shaft (5) and provided on the clutch driven side of the forward unit (2), and a reverse drive gear (7) provided on the clutch driven side of the reverse unit (3). is a large gear (8) fixed to the output shaft (5).
) are engaged with each other to perform one forward and one forward speed change. In the second forward speed, the power on the input side is passed through the clutch mechanism on the forward unit (2) side and
The transmission is transmitted to the driven side of the clutch mechanism of the speed unit (4), and the forward drive gear (6
), and the power is transmitted to the output shaft (5) via the large gear (8).

Problems to be Solved by the Invention By the way, among the propulsion systems for ships, there is a two-engine, two-shaft model in which two engines are installed and the propeller shafts are rotated in opposite directions to each other for propulsion. If you try to achieve two-stage speed change in such a two-engine, two-shaft propulsion mechanism, the rotations of the floper shafts connected to each engine will be equal and opposite to each other not only at speed but also at two consecutive speeds. It needs to be rotated at the number of revolutions. In such a case, there is a problem in that a conventional two-speed forward speed one-speed reverse speed reduction/reversing machine having the same configuration cannot handle the problem.

It is an object of the present invention to solve the above-mentioned problems and to provide a speed reduction/reversing machine that can sufficiently correspond to a two-machine, two-shaft specification.

Means for Solving the Problems The present invention, as a technical means for solving the above-mentioned problems, provides a forward unisol l-(12) and a reverse unit (25) disposed adjacent to the output shaft (18). ), in which the power from the engine is reversed and transmitted to the output shaft (18), and a driven gear (23) is arranged concentrically with the output shaft (18) so that the driven gear (23) rotates relative to each other. The forward drive gear (15) provided on the forward drive unit (12) and the reverse drive unit (12) are
25) are respectively meshed with the driven gear (23), and the engaging/disengaging operation parts (35) (36) for 1st speed and 2nd speed, with different numbers of teeth. A pair of planetary gears (29) having teeth (29a) and (29b) are disposed around the output shaft (18).

Function: 1 series mating/disassembly operation section (35) and 2 series mating/disassembly operation section (36)
) by selectively operating the driven gear (23).
The forward and backward movement power transmitted to the output shaft (18) is transmitted to the output shaft (18) via the idling gear (29) at different rotational speeds.

Example Embodiments of the present invention will be described below based on the drawings.

1 to 3 show a first embodiment of the present invention.

In Fig. 1, (10) indicates the deceleration/reversing machine case;
A forward shaft (11) serving as an input shaft is rotatably supported on the upper side of the speed reduction/reversing machine case (10) so as to be rotatable in the front and rear directions. The front end of the forward shaft (11) protrudes forward through the speed reducer/reverser case (10), and is connected to an engine (not shown) via a shaft coupling (not shown). .

A forward unit (12) is provided on the rear side of the forward shaft (11).
) is fixed to the forward clutch housing (13). A forward input gear (14) is formed on the outer periphery of this clutch housing (13). On the other hand, a forward pinion (15) as a forward drive gear is loosely fitted on the front side of the forward shaft (11).
) The clutch driven part (16
) is inserted into the forward clutch housing (13). A hydraulic multi-plate forward clutch (17) is provided between the clutch driven portion (16) and the forward clutch housing (13). That is, by connecting the forward clutch (17), the power from the forward clutch housing (13) is transferred to the forward small gear (15).
It is intended to be transmitted to

An output shaft (18) is disposed in the front-rear direction below the forward movement unit (12) having the above-described structure. The output shaft (18) is connected to an itl receiver (21) provided on the front wall (19) and rear wall (2o) of the speed reduction/reversing machine case (10).
) (22). The rear end portion of the output shaft (18) is connected to the reduction/reversing machine case (10).
) and protrudes rearward through the rear wall (20) of the shaft, and is connected to a propeller shaft (not shown) via a shaft joint (not shown).

On the other hand, an idler wheel (24) having a large gear (23) as a driven gear of the present invention is rotatably supported on the front end portion of the output shaft (18). That is,
The large gear (23) and the output shaft (18) are rotatable with respect to each other. The forward small gear (15) of the forward uni-sole (12) is meshed with the large gear (23).

Further, as shown in Fig. 2, a reverse unit (25) having the same structure as the forward unit (12) is arranged in the longitudinal direction on the side of the forward unit l-(12) and the output shaft (18). It is set up. The backward drive unit (25) is also provided with a clutch mechanism (not shown), and the drive side of the clutch mechanism is provided with a reverse input gear (26) of the same diameter as the forward input gear (14), On the driven side, a reverse drive gear (27) having the same diameter as the forward drive gear (15) is provided. Then, one reverse input gear (
26) into mesh with the forward input gear (14),
The other reverse small gear (27) is meshed with the large gear (23).

That is, the forward unit (12) and the reverse unit (25
) by selectively connecting the large gear (23
) will rotate in opposite directions with the same number of rotations.

Next, the structure around the output shaft (18) will be explained in more detail.

As mentioned above, the free wheel (2) is loosely supported on the output shaft (18).
4), a carrier (28) is rotatably supported. The carrier (28) has a canine part (29a) and a small tooth part (29b) having different numbers of teeth.
A series of planetary gears (29) are rotatably supported by a planetary gear shaft (48) integrally fixed to the carrier (28). The canine tooth portion (29a) on the front side is connected to the free wheel (
24) is meshed with a sun gear (30) formed at the rear end portion. The small tooth part (29b) on the rear side has an output shaft (
18) and an internal gear (31) arranged concentrically. This internal gear (31) is configured to rotate independently of the output shaft (18). In addition, the small tooth part (2
9b) includes an output gear (18) provided on the output shaft (18).
32) are engaged. Three planetary gears (29) (29) (29) having such a structure are arranged around the sun gear (30) with different phases, as shown in FIG.

Further, the large gear (23) is formed with a clutch housing portion (33) having a recessed rear side wall portion. A clutch driven portion (34) in which the boss portion of the carrier (28) projects forward is inserted into the clutch storage portion (33). And, between the clutch driven part (34) and the large gear (23), there is provided a hydraulic multi-disc type 1-speed clutch (35) as a single-stage engagement/disassembly operation part of the first embodiment.

(36) is the rear wall (20
) shows the two-brake brake as the second-speed engagement/disassembly operation unit in the first embodiment. , this second speed brake (36) includes a hydraulic piston (37) attached to the rear side wall (20), and a brake plate (38) (3B) that slides in the front and rear direction by the hydraulic piston (37).・
It is basically composed of.

A braked portion (39) provided on the internal gear (29) is interposed between the adjacent brake plates (38) (3B). Therefore, by operating the hydraulic piston (37), the brake plate (38) is moved to the braked portion (
39) to press the internal gear (29) into the deceleration and reversing gear case (
10).

Next, the power transmission path of this first embodiment will be explained.

At the time of 1st forward speed and 1st reverse speed, 1st speed Kurasochi (35
) to connect the large gear (23) and carrier (28). Then, the output shaft (18) includes the forward small gear (15) (reverse small gear (27)) - large gear (23) - (first speed clutch (35)) - carrier (28) → planetary gear (29). ) (small tooth part (29b)
) - output gear (32) - output shaft (18). In this case, the planetary gear (
29) and the sun gear (30) move together, the large gear (23) and the output shaft (18) rotate at the same speed.

During 2nd forward speed and 2nd reverse speed, the 2nd speed brake (36
) to fix the internal gear (29).

Then, the output shaft (18) has a forward small gear (15).
(Reverse small gear (27)) - Large gear (23) - Sun gear (30) - Planetary gear (29) (Canine tooth part (29a)
, small tooth portion (29b)) - output gear (32) -> output shaft (18). In that case, as mentioned above, the internal gear (29) is
0), the free gear (29) moves around the output shaft (18) while meshing with the internal gear (29). Therefore, the small teeth of the planetary gear (29) (
The rotational speed of the output gear (32) meshed with the gear 29a) is lower than that at the first speed.

3 and 4 show a second embodiment of the present invention.

In this second embodiment as well, the output shaft (18) is disposed in the front-rear direction at the lower side of the speed reduction/reversing gear case (10).
The rear end side of the output shaft (18) is connected to the reduction/reversing gear case (10).
) and protrudes rearward.

In this case as well, an idler wheel (24) is rotatably supported on the front side of the output shaft (18). and,
The front end of the idle wheel (24) is equipped with a large gear (
23) is formed. That is, also in this second embodiment, the large gear (23) and the output shaft (18) are rotatable with respect to each other.

Note that the input portion of the large gear (28) is the same as in the first embodiment. That is, the forward gear (15) of the forward unit (12) installed above the output shaft (18) and the reverse gear (27) of the reverse unit (25) installed on the side of the forward unit (12). ) is a large gear (23
) are meshed with each other.

A carrier (
28) is rotatably supported, and its carrier (28) is rotatably supported.
) The clutch driven part (34) has a boss part protruding forward.
) is inserted into the clutch accommodating portion (33) provided in the large gear (23), which is also the same as in Example 1. In the clutch storage portion (33), a hydraulic multi-disc type single clutch (35) as a first speed engagement/disengagement operation section in the second embodiment is connected to the clutch driven section (34) and the large gear (23). It is set in between.

(36) indicates a dual brake (36) as a second-speed engagement/disassembly operation section in the second embodiment, which is disposed above the carrier (28). This 2nd speed brake (36)
is fixed to the rear wall (20) of the speed reducer/reverse gear case (10) extending forward.

The brake plate (
38) A rotary plate (40) spline-fitted to the outer peripheral portion of the carrier (28) is interposed between (3B). Therefore, by operating the hydraulic piston (37), the carrier (28) is fixed to the speed reducer/reverser case (lO).

Also in this embodiment 2, the carrier (28) has a canine tooth section (29a) and a small tooth section (29a) having different numbers of teeth.
b) A pair of planetary gears (29) having the following configuration are rotatably supported by a planetary gear shaft (48) fixed to its carrier (28). Then, the canine tooth part on the front side (29
a) is meshed with a sun gear (30) formed on the rear end side of the idling shaft (24).

On the other hand, the small tooth part (29b) on the rear side is connected to the output shaft (18).
It is meshed with an output gear (32) formed in . Also in this case, three planetary gears (29) (
29) As shown in FIG. 5, the gears (29) are arranged around the sun gear (30) with different phases.

Next, a power transmission path in Example 2 will be explained.

At 1st forward speed and 2nd reverse speed, the 1st speed clutch (35)
is operated to fix the large gear (23) and carrier (18). Then, the output shaft (18) includes the forward small gear (15) (reverse small gear (27)) - the large gear (2
3) → (1st gear clutch (35) ”) → Carrier (2
) - Planetary gear (29) (small tooth part (29b))
Power is transmitted through the path: - output gear (32) - output shaft (18). In this case, the planetary gear (
29) and the sun gear (30) move together, the large gear (23) and the output shaft (18) rotate at the same speed.

During 2nd forward speed and 2nd reverse speed, 2nd speed brake (36)
The hydraulic piston (37) is operated. Then, the output shaft (18) includes the forward small gear (15) (reverse small gear (27)) - large gear (23) - sun gear (30) -
Planetary gear (29) (canine tooth part (29a), small tooth part (29b)) - Output gear (32) - Output shaft (18)
It is transmitted through this route. In this case, the carrier (2
8) is fixed to the reduction/reversing gear case (10), so the ratio of the number of teeth between the sun gear (30) and the canine tooth section (29a) and the number of teeth between the small tooth section (29b) and the output gear (32) are the same. The power that has been decelerated by the combined amount is transmitted to the output shaft (18).

6 and 7 show a third embodiment of the present invention.

In this third embodiment as well, the output shaft (18) is arranged in the front-rear direction at the lower side of the speed reduction/reversing gear case (10).
The rear end side is the rear wall (20
) and protrudes rearward.

The large gear (2
3) is a bearing (42) provided on the front side wall (19) and intermediate support wall (41) of the speed reducer/reverser case (10), respectively.
It is rotatably supported by (43).

The output shaft (18) is supported by being inserted through the cylindrical boss (44) of the large gear (23). Therefore, also in this third embodiment, the output shaft (18) and the large gear (23) rotate independently of each other.

In this third embodiment as well, the input portion of the large gear (23) is the same as in the first embodiment. That is, the forward gear (15) of the forward unit (12) installed above the output shaft (18), and the reverse gear (27) of the reverse unit (25) installed on the side of the forward unit (12).
) are meshed with the large gear (23).

Further, a carrier (4) is provided on the rear side of the output shaft (18).
5) are integrally formed. The carrier (45) has a canine tooth part (29a) and a small tooth part (29b) having different numbers of teeth.
) and a carrier (4).
It is rotatably supported on a planetary gear shaft (48) fixed to 5). The small tooth portion (29b) on the front side is connected to the large gear (
The sun gear (3) formed at the rear end of the cylindrical boss (44) of
0). The small tooth portion (29b) meshes with an internal gear for l-speed (31a) which is rotatably supported concentrically with the output shaft (18).

On the other hand, the canine tooth portion (29b-) on the rear side meshes with a second-speed internal gear (31b) which is similarly rotatably supported concentrically with the output shaft (18). In addition, in this example,
The number of teeth of the 2nd speed internal gear (31b) is the same as the 1st gear internal gear (3
The number of teeth is greater than the number of teeth in 1a). In this case as well, three planetary gears (29) (29) (29)
are arranged around the sun gear (30) with different phases, as shown in FIG.

Further, (46) indicates a single-brake brake as a first-speed engagement/disassembly operation section in this third embodiment, and (47) indicates a two-branch brake as a two-speed engagement/disassembly operation section. These first speed brake (46) and double brake (47) are connected to the intermediate support wall (41) and the rear in correspondence with the first speed internal gear (31a) and second speed internal gear (31b'). The l-speed brake (4) is installed between the side wall (20) and the intermediate support wall (41).
By operating the hydraulic piston (37) of 6),
A brake plate (38) attached so as to be slidable in the front and back is pressed against a braked portion (39) of the single-set internal gear (31a), thereby fixing the single-set internal gear (31a). Also,
By operating the hydraulic piston (37) of the 2nd speed brake (47) fixed to the rear side wall (20), the brake plate (38), which is similarly attached so as to be slidable back and forth, is activated by the 2nd speed internal gear ( The second gear internal gear (31b) is fixed by pressing against the braked portion (39) of the second gear (31b).

Next, a power transmission path in Example 3 will be explained.

At 1 forward speed and 1 reverse speed, 1 continuous brake (46)
The hydraulic piston (37) is operated. Then, 1
The continuous internal gear (31a) is fixed to the reduction/reversing gear case (10), and the forward small gear (15) (reverse small gear (27)) - large gear (23) - sun gear (30) - idling gear ( Power is transmitted to the output shaft (18) through the path 29) - carrier (45) - output shaft (8). In this case, the small tooth portion (29a) of the free gear (29) is transferred while meshing with the l-speed internal gear (31a). Therefore, the rotating plate of the output shaft (18) is connected to the large gear (
23).

When in 2 forward speeds and 2 reverse speeds, the 2nd speed brake (48)
actuate the hydraulic piston (37) of the 2nd speed internal gear (
31b) is fixed to the reducer/reverse gear case (10). Then, this time, the large tooth part (2) of the planetary gear (29)
9a) transfers while meshing with the 2nd gear internal gear (31b), which has more teeth than the 1st gear internal gear (31a), so the power is transmitted to the sun gear (30) through the same route as in 1st gear. However, the output shaft (18) is decelerated to a greater extent than at l speed.
It will be transmitted to

As described above, in the present invention, the output shaft portion of the speed reduction/reversing machine is
By providing a 1-set engagement/disassembly operation section and a 2-section engagement/disassembly operation section, power is transmitted to the output shaft via two planetary gears with different numbers of teeth also provided on the output shaft portion. By making the rotational speeds transmitted from the forward and reverse units the same in both forward and reverse directions, it is possible to easily obtain a two-speed forward and reverse marine speed reducer and reverse gear that has the same reduction ratio in forward and reverse directions. Therefore, there is an advantage that a two-engine, two-shaft specification in which the propeller shafts rotate in opposite directions can be realized very easily. Moreover, since the first and second speeds are shifted at the output shaft portion, there is an advantage that clutch mechanisms having the same capacity can be used for the forward unit and the reverse unit, thereby preventing slippage.

Furthermore, the parts other than the output shaft portion can be used for both forward and reverse one-speed transmission, increasing the number of parts that can be used in common, which has the advantage of reducing manufacturing costs.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view of Embodiment 1 of the present invention, FIG. 2 is a schematic diagram showing the meshing state of the forward unit, reverse unit, and large gears, and FIG. 3 is the gears around the output shaft. FIG. 2 is a schematic diagram showing a state of engagement. FIG. 4 is a longitudinal sectional view of the second embodiment, and FIG. 5 is a schematic diagram showing the meshing state of gears around the output shaft. Figure 6 shows
FIG. 7, a longitudinal cross-sectional view of the third embodiment, is a schematic diagram showing the arrangement of gears around the output shaft. FIG. 8 is a schematic diagram showing a conventional example. (12)...Forward unit, (15)...Forward small gear, (18)...Output shaft, (23)...Large gear, (
25)... Reverse unit, (27)... Reverse small gear, (29)... Planetary gear, (35)... 1st gear clutch, (36)... 2nd gear brake, ( 46)...
Brake for l speed. Figure 3

Claims (1)

[Claims] In an apparatus in which the power from the engine is reversed and transmitted to the output shaft by a forward unit and a reverse unit arranged adjacent to the output shaft, a driven gear is arranged concentrically with the output shaft and a forward drive gear rotatably supported and provided on the forward unit;
Similarly, reverse drive gears provided in the reverse unit are meshed with the driven gears, respectively, and a pair of planetary gears each having an engagement/disassembly operation section for 1st speed and 2nd speed, and a pair of planetary gears having different numbers of teeth of different sizes. is arranged around the output shaft.