CN216555174U

CN216555174U - Marine gearbox with fast and slow gear output

Info

Publication number: CN216555174U
Application number: CN202220088359.9U
Authority: CN
Inventors: 陈王龙
Original assignee: Hangzhou Xiaoshan Jiangnan General Machinery Co ltd
Current assignee: Hangzhou Xiaoshan Jiangnan General Machinery Co ltd
Priority date: 2022-01-13
Filing date: 2022-01-13
Publication date: 2022-05-17
Anticipated expiration: 2032-01-13

Abstract

The utility model discloses a marine gearbox with high and low gear output, which relates to the field of marine gearboxes and comprises a box body, wherein a reversing shaft, an input shaft and an output shaft are arranged in the box body; the flywheel of the diesel engine is connected with one end of the input shaft through an input coupling for transmission, a slow gear transmission gear is fixedly arranged on the input shaft close to the input coupling, and a slow gear piston, a slow gear return spring and a slow gear inner friction plate are arranged in the slow gear transmission gear; the input shaft is also provided with a slow-gear driving gear which rotates relatively, and a slow-gear driving gear seat of the slow-gear driving gear is provided with a slow-gear outer friction plate which is used for forming a slow-gear clutch by matching with a slow-gear inner friction plate; the slow-gear driving gear is constantly meshed with a slow-gear driven gear installed on the output shaft, and power is provided for the slow-gear following working condition of the output shaft. The utility model can simultaneously exert the maximum power of the diesel engine under the conditions of heavy load and light load of the ship; the energy consumption of the diesel engine is saved, and the time is saved. The maximum economic benefit is brought into play.

Description

Marine gearbox with fast and slow gear output

Technical Field

The utility model relates to the field of marine gear boxes, in particular to a marine gear box with a high-speed gear and a low-speed gear output.

Background

At present, the marine gearbox only has one output rotating speed and two steering directions, namely forward driving or reverse driving. The forward driving has only one output rotating speed, and the reverse driving has only one output rotating speed. Usually the diesel engine power used in the design of a ship is determined according to the maximum required power of the ship, under which power the rotational speed of the propeller is also determined. The ship can reach the requirement when must satisfy the heavy load operating mode under the heavy load condition, if the thrust isoparametric of screw confirms, but the navigation speed of ship depends on the rotational speed of screw simultaneously in certain extent, screw displacement promptly, the higher displacement that screw rotational speed is, the more fast is sailed of ship promptly, so when the navigation of boats and ships was in the light load operating mode, the resistance of ship is little a lot, just can increase the rotational speed of screw, improves the navigation speed of boats and ships. The utility model aims to increase the rotating speed of a propeller under the condition that a ship meets the power condition of a diesel engine under a heavy-load working condition and under a light-load working condition, and use the power of the diesel engine. The sailing is faster under light load, the fuel is saved, the time is saved, and the efficiency is improved.

SUMMERY OF THE UTILITY MODEL

The utility model aims to overcome the defects in the prior art and provide a gearbox for a high-speed and low-speed output ship. When the ship is full or the trawl is in working condition, the fast clutch is disengaged, and the slow clutch is combined, so that the diesel engine runs at full power when the ship is full and the heavy load is met. The parameters of the propeller such as disc surface ratio, rotating speed, helical angle and the like are matched with the resistance in water of the ship body and the power of the diesel engine in design. The diesel engine meets the power of heavy load working condition. When the light load working condition is adopted, the rotating speed of the propeller is increased when the resistance of the ship is reduced, the sailing speed of the ship can be increased within the same power range of the diesel engine, and the effects of saving time and oil are achieved.

The purpose of the utility model is achieved by the following technical scheme: the marine gearbox with the high-speed gear and the low-speed gear comprises a box body, wherein a reversing shaft, an input shaft and an output shaft are arranged in the box body; the flywheel of the diesel engine is connected with one end of the input shaft for transmission through an input coupling, a slow gear transmission gear is fixedly arranged on the input shaft close to the input coupling, and a slow gear piston, a slow gear return spring and a slow gear inner friction plate are arranged in the slow gear transmission gear; the input shaft is also provided with a slow-gear driving gear which rotates relatively, and a slow-gear outer friction plate is arranged on a slow-gear driving gear seat of the slow-gear driving gear and is used for being matched with a slow-gear inner friction plate to form a slow-gear clutch; the slow-gear driving gear is normally meshed with a slow-gear driven gear arranged on the output shaft to provide power for the slow-gear running working condition of the output shaft;

the slow gear transmission gear is normally meshed with the reversing transmission gear, the reversing transmission gear is fixedly arranged at one end, close to the input coupling, of the reversing axle, and a reversing piston, a reversing return spring and a reversing inner friction plate are arranged in the reversing transmission gear; a reverse driving gear which rotates relatively is also arranged on the reverse shaft, and a reverse driving outer friction plate is arranged on a reverse driving gear seat of the reverse driving gear and is used for being matched with a reverse inner friction plate to form a reverse clutch; the reversing driving gear is normally meshed with a slow-gear driven gear arranged on the output shaft to provide power for the slow-gear reversing working condition of the output shaft;

a quick-gear clutch shell is fixedly arranged at one end of the input shaft, which is far away from the input coupling, and a quick-gear piston, a quick-gear return spring and a quick-gear inner friction plate are arranged in the quick-gear clutch shell; the input shaft is also provided with a relatively rotating fast gear driving gear, and a fast gear driving gear seat of the fast gear driving gear is provided with a fast gear outer friction plate which is used for being matched with a fast gear inner friction plate to form a fast gear clutch; the fast-gear driving gear is constantly meshed with a fast-gear driven gear fixedly arranged on the output shaft to provide power for the fast-gear smooth working condition of the output shaft;

the output shaft outputs power outwards through the output coupling, an oil pump is further arranged on the box body, and the oil pump supplies oil to the reversing shaft and the input shaft under the control of the control valve.

As a further technical scheme, the reverse axle is supported on the box body through a bearing A and a bearing B, a reversing oil inlet cover is mounted at one end cover of the reverse axle, which is far away from the input coupling, and the oil pump is communicated with a reversing working oil way of the reverse axle through the reversing oil inlet cover and supplies oil for a gear box slow gear reversing working condition.

As a further technical scheme, the input shaft is supported on the box body through a bearing C and a bearing F, an in-vehicle oil inlet cover is mounted at one end cover of the input shaft, which is far away from the input coupling, and the oil pump is communicated with an in-vehicle working oil circuit of the input shaft through the in-vehicle oil inlet cover to supply oil for the working conditions of slow-gear in-vehicle and fast-gear in-vehicle of the gearbox.

As a further technical scheme, one end of the input shaft, which is far away from the input coupling, is positioned with the box body through a positioning plate.

As a further technical scheme, one end of the input shaft, which is close to the input coupling, is provided with an input flange, and the input coupling is fixedly arranged on the input flange.

As a further technical solution, the output shaft is supported by the case through a bearing D and a bearing E.

As a further technical scheme, the slow-gear driven gear and the fast-gear driven gear can be detachably mounted on the output shaft, and the speed ratio of the gear box is adjusted by changing the tooth numbers of the slow-gear driven gear and the fast-gear driven gear, namely the rotating speed output by the output shaft is adjusted.

As a further technical solution, the slow gear driving gear is disposed on the input shaft near the fast gear driving gear, so that the slow gear driven gear is also disposed on the output shaft near the fast gear driven gear.

The utility model has the beneficial effects that: the maximum power of the diesel engine can be exerted under the conditions of heavy load of the ship and light load of the ship; the energy consumption of the diesel engine is saved, and the time is saved. The maximum economic benefit is brought into play.

Drawings

FIG. 1 is a schematic structural diagram of the present invention.

Fig. 2 is a sectional view a-a of fig. 1.

Fig. 3 is a schematic structural view of the inverted axle of the present invention.

Fig. 4 is a schematic structural view of an input shaft in the present invention.

Fig. 5 is a schematic structural view of an output shaft of the present invention.

Description of reference numerals: 1. a control valve; 2. an oil pump; 3. a box body; 4. a reverse return spring; 5. a reverse drive gear seat; 6. a bearing A; 7. a reverse drive gear; 8. a reversing piston; 9. a reversing outer friction plate; 10. a reversing inner friction plate; 11. a reverse drive gear; 12. a reversing shaft; 13. a reversing oil inlet cover; 14. a bearing B; 15. an oil inlet cover is arranged in front of the vehicle; 16. a fast gear driving gear; 17. positioning a plate; 18. an input shaft; 19. a bearing C; 20. an output coupling; 21. a quick-shift piston; 22. a bearing D; 23. a fast-gear inner friction plate; 24. a fast-gear outer friction plate; 25. a fast-gear driven gear; 26. a fast clutch housing; 27. a slow-gear driven gear; 28. a quick return spring; 29. a fast-gear driving gear seat 30 and an output shaft; 31. a bearing E; 32. a slow gear drive gear; 33. a slow-gear driving gear seat; 34. a bearing F; 35. an input coupling; 36. a slow gear return spring; 37. an input flange; 38. a slow gear transmission gear; 39. a slow gear piston; 40. a slow-gear inner friction plate; 41. a slow gear outer friction plate; 42. a slow speed clutch; 43. a fast clutch; 44. a reverse clutch; 45. a reversing working oil way; 46. the working oil circuit is followed.

Detailed Description

The utility model will be described in detail below with reference to the following drawings:

example (b): as shown in attached figures 1-5, the marine gearbox with the fast and slow gears for output comprises a box body 3, wherein a reversing shaft 12, an input shaft 18 and an output shaft 30 are arranged in the box body 3. Referring to fig. 2, a diesel engine flywheel is connected with one end of the input shaft 18 through an input coupling 35 for transmission, a slow gear transmission gear 38 is fixedly arranged on the input shaft 18 close to the input coupling 35, and a slow gear piston 39, a slow gear return spring 36 and a slow gear inner friction plate 40 are arranged in the slow gear transmission gear 38. The input shaft 18 is also provided with a relatively rotating (i.e. free) slow gear driving gear 32, and a slow gear outer friction plate 41 is arranged on a slow gear driving gear seat 33 of the slow gear driving gear 32 and is used for cooperating with a slow gear inner friction plate 40 to form a slow gear clutch 42. The slow speed drive gear 32 is in constant mesh with the slow speed driven gear 27 mounted on the output shaft 30 to provide power for the slow speed ride through condition of the output shaft 30.

The slow gear transmission gear 38 is normally meshed with the reverse transmission gear 7, the reverse transmission gear 7 is fixedly arranged at one end, close to the input coupling 35, of the reverse axle 12, and a reverse piston 8, a reverse return spring 4 and a reverse inner friction plate 10 are arranged in the reverse transmission gear 7. As shown in fig. 2 and 3, a reverse driving gear 11 which rotates relatively (i.e. is free) is further mounted on the reverse axle 12, and a reverse outer friction plate 9 is disposed on a reverse driving gear seat 5 of the reverse driving gear 11, and is used for cooperating with a reverse inner friction plate 10 to form a reverse clutch 44. The reverse driving gear 11 is normally engaged with a slow gear driven gear 27 mounted on the output shaft 30 to provide power for the slow gear reverse operation condition of the output shaft 30.

As shown in fig. 4, a fast clutch outer 26 is fixedly mounted on an end of the input shaft 18 away from the input coupling 35, and a fast piston 21, a fast return spring 28 and a fast inner friction plate 23 are arranged in the fast clutch outer 26. The input shaft 18 is also provided with a relatively rotating (i.e. free) fast driving gear 16, and a fast driving gear seat 29 of the fast driving gear 16 is provided with a fast outer friction plate 24 for cooperating with a fast inner friction plate 23 to form a fast clutch 43. The fast-gear driving gear 16 is normally meshed with a fast-gear driven gear 25 fixedly arranged on the output shaft 30, and provides power for the fast-gear forward working condition of the output shaft 30.

As shown in fig. 1 and 5, the output shaft 30 outputs power to the outside through an output coupling 20, the housing is further provided with an oil pump 2, and the oil pump 2 supplies oil to the countershaft 12 and the input shaft 18 under the control of the control valve 1. The output shaft 30 is supported by the case 3 via a bearing D22 and a bearing E31.

Referring to the attached drawing 2, the reverse axle 12 is supported on the box body 3 through a bearing A6 and a bearing B14, one end cover of the reverse axle 12, which is far away from the input coupling 35, is provided with a reverse oil inlet cover 13, and the oil pump 2 is communicated with a reverse working oil path 45 of the reverse axle 12 through the reverse oil inlet cover 13 to supply oil for the slow gear reverse working condition of the gearbox. The input shaft 18 is supported on the box body 3 through a bearing C19 and a bearing F34, an in-vehicle oil inlet cover 15 is arranged at one end of the input shaft 18, which is far away from the input coupling 35, and the oil pump 2 is communicated with an in-vehicle working oil path 46 of the input shaft 18 through the in-vehicle oil inlet cover 15 to supply oil for the slow-gear in-vehicle working condition and the fast-gear in-vehicle working condition of the gearbox. The end of the input shaft 18 facing away from the input coupling 35 is positioned with the housing 3 by means of a positioning plate 17. An input flange 37 is provided at one end of the input shaft 18 adjacent the input coupling 35, and the input coupling 35 is fixedly mounted to the input flange 37.

Preferably, the slow driven gear 27 and the fast driven gear 25 are both detachably mounted on the output shaft 30, and the speed ratio of the gear box, that is, the rotation speed output by the output shaft 30, is adjusted by changing the number of teeth of the slow driven gear 27 and the fast driven gear 25. Therefore, the speed ratio of the gearbox can be changed along with the replacement of the gear on the same gearbox, and the gearbox is not limited by other conditions, such as the hole pitch of the box body and the like.

The slow drive gear 32 is disposed on the input shaft 18 adjacent to the fast drive gear 16 such that the slow driven gear 27 is also disposed on the output shaft 30 adjacent to the fast driven gear 25. The utility model arranges the fast clutch 43 and the slow clutch 42 of the gear box on the same input shaft 18, and leads the fast and slow driven

gears

25 and 27 to lean against each other, thereby effectively saving the axial space of the gear box, and leading the gear box to have the smallest volume and the lightest weight. In addition, the utility model arranges two sets of clutches (namely the slow clutch 42 and the reverse clutch 44) under heavy-load working conditions at one end of the gearbox close to the diesel engine, so that the stress on the box body is uniform.

The working process of the utility model is as follows: the utility model has three working conditions of slow gear forward driving, slow gear reverse driving and fast gear forward driving.

Slow gear forward driving: the diesel engine is connected with the driving input shaft 18 through an input coupling 35 of the gearbox to rotate, and in a slow-gear forward working condition, the control valve 1 controls the oil pump 2 to deliver gearbox working oil to a forward working oil path 46 of the input shaft 18, so that the slow-gear piston 39 presses the slow-gear inner friction plate 40 and the slow-gear outer friction plate 41, namely the slow-gear clutch 42 to be combined. The slow drive gear 32 rotates with the slow drive gear 38 and rotates the intermeshed slow driven gear 27, as does the output shaft 30. Because the output coupling 20 is fixedly arranged at the end part of the output shaft 30, the power of the diesel engine can be transmitted to the propeller connected with the output shaft, and the working condition of slow and heavy-load navigation of the ship is completed. At this time, the gear box clutch 43 retracts the shift piston 21 by the shift return spring 28, and the shift clutch 43 is disengaged. At the same time, the reverse clutch 44 retracts the reverse piston 8 under the action of the reverse return spring 4, and the reverse clutch 44 is also in a disengaged state.

Reversing in a slow gear mode: since the slow drive gear 38 and the reverse drive gear 7 are in constant mesh with each other, the reverse drive gear 7 rotates when the input shaft 18 rotates. When the reversing is in a slow gear working condition, the control valve 1 controls the oil pump 2 to deliver the gear box working oil to the reversing working oil path 45 of the reversing shaft 12, so that the reversing piston 8 presses the reversing inner friction plate 10 and the reversing outer friction plate 9, namely the reversing clutch 44 is combined. The reverse driving gear 11 rotates along with the reverse transmission gear 7 to drive the engaged slow gear driven gear 27 to rotate, and the output shaft 30 also rotates together. The output shaft 30 transmits the power of the diesel engine to the propeller through the output coupling 20, and the reverse sailing condition (generally used when leaning against a wharf) of the ship is completed. At this time, the quick piston 21 in the quick clutch 43 of the gear box is retracted by the quick return spring 28, and the quick clutch 43 is disengaged. At the same time, the slow piston 39 of the slow clutch 42 is retracted by the slow return spring 36, and the slow clutch 42 is also disengaged.

And (3) fast-gear forward driving: when the vehicle runs in the fast gear, the control valve 1 controls the oil pump 2 to deliver the gear box working oil to the running working oil path 46 of the input shaft 18, so that the fast gear piston 21 presses the fast gear inner friction plate 23 and the fast gear outer friction plate 24, namely the fast gear clutch 43 is combined. The forward drive gear 16 begins to rotate with the forward clutch housing 26 and rotates the intermeshing forward driven gear 25, along with the output shaft 30. The output shaft 30 transmits the power of the diesel engine to the propeller through the output coupling 20, and the fast sailing working condition of the ship is completed. At this time, the slow piston 39 in the slow clutch 42 of the gearbox is retracted by the slow return spring 36, and the slow clutch 42 is disengaged. The reverse piston 8 of the reverse clutch 44 is retracted by the reverse return spring 4, and the reverse clutch 44 is in a disengaged state.

The ship is combined by the fast clutch 43 when in light-load navigation or non-trawling working condition, the propeller rotating speed of the ship is improved, and the fast navigation is realized. When the ship enters a port or needs to be reversed, the control valve 1 controls the slow clutch 42 or the reverse clutch 44 to be combined, and the slow forward and reverse stop working condition is carried out.

The utility model has the structural characteristics that three working conditions of the gear box are independently controlled by three sets of clutches, and two sets of clutches (namely a slow clutch 42 and a reverse clutch 44) under heavy-load working conditions are arranged at one end of the gear box close to the diesel engine, so that the stress of the box body is uniform. The fast clutch 43 and the slow clutch 42 of the gear box are arranged on the same input shaft 18, and the fast and slow driven

gears

25 and 27 are close to each other, so that the axial space of the gear box is effectively saved, the size of the gear box is reduced, and the weight of the gear box is lightened. The fast clutch of the gear box is arranged at the rear end of the input shaft due to no transmission gear arrangement and no radial force, and utilizes the spline to transmit torque, so that the fast clutch is easy to disassemble and assemble. The design of the gearbox realizes that the speed ratio of the gearbox can be changed along with the replacement of the gear on the same gearbox, and is not limited by other conditions, such as the hole pitch of the box body and the like. The control valve of the gear box is designed as a combined multi-station compound valve.

It should be understood that equivalent alterations and modifications of the technical solution and the inventive concept of the present invention by those skilled in the art should fall within the scope of the appended claims.

Claims

1. The utility model provides a marine gear box of fast slow-speed fender output which characterized in that: comprises a box body (3), wherein a reversing shaft (12), an input shaft (18) and an output shaft (30) are arranged in the box body (3); a flywheel of the diesel engine is connected with one end of the input shaft (18) through an input coupling (35) for transmission, a slow gear transmission gear (38) is fixedly arranged on the input shaft (18) close to the input coupling (35), and a slow gear piston (39), a slow gear return spring (36) and a slow gear inner friction plate (40) are arranged in the slow gear transmission gear (38); the input shaft (18) is also provided with a slow gear driving gear (32) which rotates relatively, and a slow gear outer friction plate (41) is arranged on a slow gear driving gear seat (33) of the slow gear driving gear (32) and is used for being matched with a slow gear inner friction plate (40) to form a slow gear clutch (42); the slow gear driving gear (32) is normally meshed with a slow gear driven gear (27) arranged on the output shaft (30) to provide power for the slow gear forward working condition of the output shaft (30);

the slow gear transmission gear (38) is normally meshed with the reversing transmission gear (7), the reversing transmission gear (7) is fixedly arranged at one end, close to the input coupling (35), of the reversing axle (12), and a reversing piston (8), a reversing return spring (4) and a reversing inner friction plate (10) are arranged in the reversing transmission gear (7); a reverse driving gear (11) which rotates relatively is also arranged on the reverse shaft (12), and a reverse outer friction plate (9) is arranged on a reverse driving gear seat (5) of the reverse driving gear (11) and is used for being matched with a reverse inner friction plate (10) to form a reverse clutch (44); the reversing driving gear (11) is normally meshed with a slow-gear driven gear (27) arranged on an output shaft (30) to provide power for the slow-gear reversing working condition of the output shaft (30);

a quick-gear clutch shell (26) is fixedly arranged at one end of the input shaft (18) deviating from the input coupling (35), and a quick-gear piston (21), a quick-gear return spring (28) and a quick-gear inner friction plate (23) are arranged in the quick-gear clutch shell (26); a fast-gear driving gear (16) which rotates relatively is further mounted on the input shaft (18), and a fast-gear outer friction plate (24) is arranged on a fast-gear driving gear seat (29) of the fast-gear driving gear (16) and is used for being matched with a fast-gear inner friction plate (23) to form a fast-gear clutch (43); the fast-gear driving gear (16) is normally meshed with a fast-gear driven gear (25) fixedly arranged on the output shaft (30) to provide power for the fast-gear forward working condition of the output shaft (30);

the output shaft (30) outputs power to the outside through an output coupling (20), the box body is also provided with an oil pump (2), and the oil pump (2) supplies oil to the reversing shaft (12) and the input shaft (18) under the control of the control valve (1).

2. The gearbox for marine vessels of claim 1, wherein: the reversing shaft (12) is supported on the box body (3) through a bearing A (6) and a bearing B (14), a reversing oil inlet cover (13) is installed at one end cover of the reversing shaft (12) departing from the input coupling (35), and the oil pump (2) is communicated with a reversing working oil way (45) of the reversing shaft (12) through the reversing oil inlet cover (13) to supply oil for a gear box slow-gear reversing working condition.

3. The marine gearbox of claim 1, wherein: the input shaft (18) is supported on the box body (3) through a bearing C (19) and a bearing F (34), an in-vehicle oil inlet cover (15) is mounted at one end cover, deviating from the input coupling (35), of the input shaft (18), and the oil pump (2) is communicated with an in-vehicle working oil path (46) of the input shaft (18) through the in-vehicle oil inlet cover (15) to supply oil for the gear box in the working conditions of slow-gear in-vehicle and fast-gear in-vehicle.

4. The marine gearbox of claim 1, wherein: one end of the input shaft (18) departing from the input coupling (35) is positioned with the box body (3) through a positioning plate (17).

5. The marine gearbox of claim 1, wherein: an input flange (37) is arranged at one end, close to the input coupling (35), of the input shaft (18), and the input coupling (35) is fixedly installed on the input flange (37).

6. The marine gearbox of claim 1, wherein: the output shaft (30) is supported by the case (3) via a bearing D (22) and a bearing E (31).

7. The gearbox for the fast and slow gear output ship according to any one of claims 1 to 6, wherein: the slow-gear driven gear (27) and the fast-gear driven gear (25) can be detachably mounted on the output shaft (30), and the speed ratio of the gear box, namely the rotating speed output by the output shaft (30), is adjusted by changing the tooth numbers of the slow-gear driven gear (27) and the fast-gear driven gear (25).

8. The gearbox for the fast and slow gear output ship according to any one of claims 1 to 6, wherein: the slow drive gear (32) is arranged on the input shaft (18) close to the fast drive gear (16) so that the slow driven gear (27) is also arranged on the output shaft (30) close to the fast driven gear (25).