CN217301339U

CN217301339U - Gearbox clutch for flexible ship

Info

Publication number: CN217301339U
Application number: CN202220569202.8U
Authority: CN
Inventors: 顾海港; 顾嘉桢; 陈明文; 周焕辉
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-03-16
Filing date: 2022-03-16
Publication date: 2022-08-26
Anticipated expiration: 2032-03-16

Abstract

The utility model relates to a flexible marine gear box clutch belongs to marine gear box technical field, the load simulator comprises a transmission shaft, transmission shaft one side be equipped with the arbor gear that is the integration with the transmission shaft, another side of transmission shaft be equipped with the clutch assembly of the movable crimping of transmission shaft looks, clutch assembly and transmission shaft between be equipped with the separation and reunion spline that is the integration with the transmission shaft, clutch assembly on be equipped with input driven gear, the transmission shaft in be equipped with the lubricating oil passageway that is linked together with the separation and reunion spline, separation and reunion spline rear end be equipped with the nested sealed lubricating oil seal assembly of transmission shaft looks. Has the characteristics of compact structure, good stability and long service life. The service life of a clutch bearing and the limit rotating speed of the clutch are prolonged, the oil pressure between friction plates of the clutch is improved, the row connection impact of the clutch is reduced, the temperature rise inside the clutch is reduced, and the early damage of the bearing is reduced.

Description

Gearbox clutch for flexible ship

Technical Field

The utility model relates to a marine gear box technical field, concretely relates to flexible marine gear box clutch.

Background

The life of a ship is typically 15 to 20 years, and some even 30 years. The service life of the marine gearbox is usually less than 15 years, and the design life of the marine gearbox is only thousands of hours after continuous use. The actual service life is far from the design life due to design, manufacturing reasons and improper use.

The marine large gearbox GWC series clutch component is in a statically indeterminate structure with bearing support after clutch connection and arrangement, and 4 bearings are arranged on the same axis. After the bearing rollers at the two ends of the shaft gear of the clutch component are subjected to factory test, the obvious damage trace ratio on the rollers is higher, and particularly the damage of a gear box with higher power is more obvious, so that the service life is influenced. And the self-aligning roller bearing on the clutch shell of the clutch component has no damage. Marine big gear box GWC series gear box has an inherent hard injury, or hidden trouble.

The coaxiality of the shaft line of the clutch bearing hole of the forward clutch component and the shaft line of the shaft gear bearing hole of the reverse clutch component is too large and exceeds the allowable inclination angle of the bearing; the clutch seat and the gear transmission shaft are in interference connection and are a rigid body (in the scheme, the clutch seat and the gear transmission shaft are connected by splines, but the two ends of the clutch seat and the gear transmission shaft are positioned by matching cylindrical surfaces. Before the clutch is connected, the clutch and the shaft gear are independent, and the rolling bearing is not subjected to additional dynamic load. After the clutch is connected, if the friction plate does not slide, the clutch and the shaft gear can be regarded as a rigid whole, the rolling bearing is subjected to a large additional dynamic load, so that the friction plate slides slightly (the service life of the friction plate is influenced), and the rolling bearing is also subjected to a large additional dynamic load; when not connected, the additional dynamic load is not applied. The difference in coaxiality also causes a swinging of the shaft, which causes a swinging of the bearing. Because the rigidity of the gear shaft is very high, the load on the bearing caused by the deformation of the shaft is also very high, and because the bearing far away from the clutch is far away from the swing center, the displacement of the inner ring of the bearing is relatively large, the micro-motion is generated between the roller and the bearing raceway, and after the micro-motion fatigue limit value is exceeded, the micro-motion damage is caused. And the bearing close to the clutch is close to the swing center, the displacement of the inner ring of the bearing is small, the micro-motion fatigue limit value is not exceeded, and micro-motion damage is not caused. This is why one bearing on the gear shaft is damaged while the other bearing is intact. Therefore, the forward bearing is damaged more heavily and the reverse bearing is damaged less heavily when the test run is carried out under an empty load, and the forward bearing is damaged seriously and the reverse bearing is damaged less heavily when the test run is carried out on a real ship. The temperature of the bearing rises due to fretting damage, which causes the material to soften. When the softer material is jogged, the rolling shaft bears the action of overload or impact load, so that the contact part of the inner ring and the outer ring and the rolling body generates plastic deformation-indentation, and severe plastic deformation occurs. After repeated extrusion, plastic deformation is aggravated, and the bearing raceway and the roller generate plastic flow. The vibration and noise of the bearing are increased, the temperature is increased, the mushroom damage is aggravated, and the running precision is reduced, so that the bearing completely fails.

The product is also connected between the gear transmission shaft and the clutch seat by a spline, but the gear transmission shaft and the clutch seat are positioned by a check ring for a common shaft, so that a large amount of lubricating oil leaks away from the clearance of the spline, the oil pressure between friction plates of the clutch is reduced, the abrasion of the friction plates is increased, the service life of the clutch is shortened, and the limit rotating speed of the clutch is reduced. Or the two ends of the spline are positioned by cylindrical transition fit, and the mode is the same as the original taper interference fit, so that additional dynamic load of the bearing can be caused.

Disclosure of Invention

The utility model discloses there is the not enough of poor stability and life weak point among the main prior art of solving, provides a gear box clutch for flexible ship, and it has compact structure, the good and long service life's of stability characteristics. The service life of a clutch bearing and the limit rotating speed of the clutch are prolonged, the oil pressure between friction plates of the clutch is improved, the row connection impact of the clutch is reduced, the temperature rise inside the clutch is reduced, and the early damage of the bearing is reduced.

The above technical problem of the present invention can be solved by the following technical solutions:

the utility model provides a gear box clutch for flexible ship, includes the transmission shaft, transmission shaft one side be equipped with the shaft gear who is the integration with the transmission shaft, another side of transmission shaft be equipped with the movable crimping's of transmission shaft clutch assembly, clutch assembly and transmission shaft between be equipped with and be the separation and reunion spline of integration with the transmission shaft, clutch assembly on be equipped with input driven gear, the transmission shaft in be equipped with the lubricating oil passageway that is linked together with the separation and reunion spline, separation and reunion spline rear end be equipped with the nested sealed lubricating oil seal assembly of transmission shaft.

Preferably, the lubricating oil sealing assembly comprises a check ring outer sleeve, and a halved inner sleeve is arranged between the check ring outer sleeve and the transmission shaft.

Preferably, the split inner sleeves form an annular structure by an upper half inner sleeve and a lower half inner sleeve.

Preferably, an O-shaped ring which is in embedded sleeve joint with the halved inner sleeve is arranged between the halved inner sleeve and the retainer ring outer sleeve.

Preferably, the clutch assembly comprises a clutch seat engaged and inserted with the clutch spline in a tooth form, a clutch outer shell sleeved with the clutch seat is arranged on the clutch seat, a clutch friction plate is arranged between the clutch outer shell and the clutch seat, a clutch oil cylinder connected and fixed with the clutch outer shell is arranged at the rear end of the clutch friction plate, and a piston is arranged between the clutch oil cylinder and the clutch friction plate.

Preferably, the front end of the clutch oil cylinder is provided with a piston guide seat movably nested with the piston and fixedly connected with the clutch oil cylinder through bolts, the piston guide seat is provided with a plurality of disc springs sleeved with the piston guide seat, and a disc spring limiting shaft sleeve fixedly connected with the piston guide seat through sleeved bolts is arranged between the disc springs and the piston guide seat.

Preferably, an oil pump shaft penetrating through the lubricating oil channel and in threaded sleeve connection with the piston guide seat is arranged at the front end of the piston guide seat, sealing plates in sleeve connection with the clutch seat and the oil pump shaft are arranged between the piston guide seat and the transmission shaft, and sealing rings in sleeve connection with the sealing plates in a clamping manner are arranged between the sealing plates and the clutch seat and between the sealing plates and the transmission shaft.

Preferably, the front end of the clutch seat is provided with a clutch flange which is in limit movable sleeve joint with the transmission shaft, the clutch flange is provided with a plurality of short unloading bolts in threaded sleeve joint with the clutch shell, and the clutch oil cylinder is provided with a plurality of long unloading bolts in threaded sleeve joint with the clutch shell.

Preferably, bearings are arranged at two ends of the shaft gear and at two sides of the clutch assembly.

Preferably, the bearing is an elastic roller bearing, a deep-cavity solid roller bearing, an elastic hollow roller bearing, an elastic deep-cavity hollow roller bearing or an elastic composite roller bearing.

The utility model discloses can reach following effect:

the utility model provides a gear box clutch for flexible ship compares with prior art, has compact structure, stable good and long service life's characteristics. The service life of a clutch bearing and the limit rotating speed of the clutch are prolonged, the oil pressure between friction plates of the clutch is improved, the row connection impact of the clutch is reduced, the temperature rise inside the clutch is reduced, and the early damage of the bearing is reduced.

Drawings

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

Fig. 2 is a structural sectional view of the present invention.

Fig. 3 is a structural sectional view of the clutch assembly of the present invention.

Fig. 4 is a schematic structural diagram of the lubricating oil seal assembly of the present invention.

Fig. 5 is a schematic structural view of the halved inner sleeve of the present invention.

Fig. 6 is a structural sectional view of the halved inner sleeve in the present invention.

In the figure: the clutch comprises a bearing 1, a shaft gear 2, a transmission shaft 3, a clutch spline 4, a clutch assembly 5, an input driven gear 6, a clutch flange 7, a clutch shell 8, a piston 9, a piston guide seat 10, a clutch oil cylinder 11, a disc spring 12, a disc spring limiting shaft sleeve 13, a clutch friction plate 14, a clutch seat 15, a lubricating oil sealing assembly 16, a lubricating oil channel 17, a long unloading bolt 18, a sealing plate 19, a short unloading bolt 20, a sealing ring 21, an oil pump shaft 22, a split inner sleeve 23, an O-shaped ring 24, a retainer ring outer sleeve 25, an upper half inner sleeve 26 and a lower half inner sleeve 27.

Detailed Description

The technical solution of the present invention is further specifically described below by way of examples and with reference to the accompanying drawings.

Example (b): as shown in fig. 1-4, a gear box clutch for a flexible ship comprises a transmission shaft 3, a shaft gear 2 integrated with the transmission shaft 3 is arranged on one side of the transmission shaft 3, a clutch component 5 movably connected with the transmission shaft 3 in a pressing manner is arranged on the other side edge of the transmission shaft 3, and bearings 1 are arranged at two ends of the shaft gear 2 and two side edges of the clutch component 5. The bearing 1 adopts an elastic roller bearing, a deep-hole solid roller bearing, an elastic hollow roller bearing, an elastic deep-hole hollow roller bearing or an elastic composite roller bearing. A clutch spline 4 integrated with the transmission shaft 3 is arranged between the clutch component 5 and the transmission shaft 3, an input driven gear 6 is arranged on the clutch component 5, a lubricating oil channel 17 communicated with the clutch spline 4 is arranged in the transmission shaft 3, and a lubricating oil sealing component 16 embedded and sealed with the transmission shaft 3 is arranged at the rear end of the clutch spline 4. The lubricating oil seal assembly 16 comprises a retainer ring outer sleeve 25, and a halved inner sleeve 23 is arranged between the retainer ring outer sleeve 25 and the transmission shaft 3. An O-shaped ring 24 which is embedded and sleeved with the halved inner sleeve 23 is arranged between the halved inner sleeve 23 and the retainer ring outer sleeve 25. The halved inner sleeve 23 is formed into an annular structure by an upper half inner sleeve 26 and a lower half inner sleeve 27.

The clutch component 5 comprises a clutch seat 15 which is engaged and inserted with the clutch spline 4 in a tooth form, the front end of the clutch seat 15 is provided with a clutch flange 7, the clutch flange 7 is provided with 8 short unloading bolts 20 which are in threaded sleeve joint with the clutch shell 8, and the clutch oil cylinder 11 is provided with 8 long unloading bolts 18 which are in threaded sleeve joint with the clutch shell 8. A clutch outer shell 8 sleeved with the clutch seat 15 is arranged on the clutch seat 15, a clutch friction plate 14 is arranged between the clutch outer shell 8 and the clutch seat 15, a clutch oil cylinder 11 connected and fixed with the clutch outer shell 8 is arranged at the rear end of the clutch friction plate 14, and a piston 9 is arranged between the clutch oil cylinder 11 and the clutch friction plate 14. The front end of the clutch oil cylinder 11 is provided with a piston guide seat 10 movably nested with the piston 9 and fixedly connected with the clutch oil cylinder 11 through bolts, 5 disc springs 12 sleeved with the piston guide seat 10 are arranged on the piston guide seat 10, and a disc spring limiting shaft sleeve 13 fixedly connected with the piston guide seat 10 through a sleeved bolt is arranged between the disc springs 12 and the piston guide seat 10. An oil pump shaft 22 which penetrates through the lubricating oil channel 17 and is in spline connection with the piston guide seat 10 is arranged at the front end of the piston guide seat 10, a sealing plate 19 which is sleeved with the clutch seat 15 and the oil pump shaft 22 is arranged between the piston guide seat 10 and the transmission shaft 3, and sealing rings 21 which are sleeved with the sealing plate 19 in an embedded manner are arranged between the sealing plate 19 and the clutch seat 15 and between the sealing plate 19 and the transmission shaft 3.

In conclusion, the gearbox clutch for the flexible ship has the characteristics of compact structure, good stability and long service life. The service life of a clutch bearing and the limit rotating speed of the clutch are prolonged, the oil pressure between friction plates of the clutch is improved, the row connection impact of the clutch is reduced, the temperature rise inside the clutch is reduced, and the early damage of the bearing is reduced.

It is obvious to a person skilled in the art that the invention is not restricted to details of the above-described exemplary embodiments, but that the invention can be implemented in other specific forms without deviating from the essential characteristics of the invention. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.

In conclusion, the above description is only the specific embodiment of the present invention, but the structural features of the present invention are not limited thereto, and any person skilled in the art can make changes or modifications within the scope of the present invention.

Claims

1. A gearbox clutch for a flexible ship is characterized in that: including transmission shaft (3), transmission shaft (3) one side be equipped with and be integrated shaft gear (2) with transmission shaft (3), transmission shaft (3) opposite side be equipped with clutch assembly (5) of transmission shaft (3) movable crimping mutually, clutch assembly (5) and transmission shaft (3) within a definite time be equipped with transmission shaft (3) be the separation and reunion spline (4) of integration, clutch assembly (5) on be equipped with input driven gear (6), transmission shaft (3) in be equipped with lubricating oil passageway (17) that are linked together with separation and reunion spline (4), separation and reunion spline (4) rear end be equipped with and inlay sealed lubricating oil seal assembly (16) of cover mutually with transmission shaft (3).

2. A gearbox clutch for a flexible boat as set forth in claim 1, wherein: the lubricating oil sealing assembly (16) comprises a retainer ring outer sleeve (25), and a split inner sleeve (23) is arranged between the retainer ring outer sleeve (25) and the transmission shaft (3).

3. A gearbox clutch for a flexible boat as set forth in claim 2, wherein: the halved inner sleeve (23) is in a ring structure formed by an upper half inner sleeve (26) and a lower half inner sleeve (27).

4. A gearbox clutch for a flexible boat as set forth in claim 2, wherein: an O-shaped ring (24) which is embedded and sleeved with the halved inner sleeve (23) is arranged between the halved inner sleeve (23) and the retainer ring outer sleeve (25).

5. A gearbox clutch for a flexible boat as set forth in claim 1, wherein: clutch module (5) include with clutch spline (4) looks tooth form meshing insert clutch seat (15) of inlaying, clutch seat (15) on be equipped with clutch housing (8) that cup joint mutually with clutch seat (15), clutch housing (8) and clutch seat (15) between be equipped with clutch friction piece (14), clutch friction piece (14) rear end be equipped with and be connected fixed clutch cylinder (11) with clutch housing (8), clutch cylinder (11) and clutch friction piece (14) between be equipped with piston (9).

6. A gearbox clutch for a flexible boat according to claim 5 wherein: the front end of the clutch oil cylinder (11) is provided with a piston guide seat (10) movably nested with the piston (9) and fixedly connected with the clutch oil cylinder (11) through bolts, the piston guide seat (10) is provided with a plurality of disc springs (12) which are mutually sleeved with the piston guide seat (10), and a disc spring limiting shaft sleeve (13) fixedly connected with the piston guide seat (10) through bolts is arranged between each disc spring (12) and the piston guide seat (10).

7. A gearbox clutch for a flexible boat according to claim 6 wherein: the oil pump is characterized in that an oil pump shaft (22) which penetrates through a lubricating oil channel (17) and is in spline connection with the piston guide seat (10) is arranged at the front end of the piston guide seat (10), a sealing plate (19) which is sleeved with the clutch seat (15) and the oil pump shaft (22) is arranged between the piston guide seat (10) and the transmission shaft (3), and sealing rings (21) which are sleeved with the sealing plate (19) in an embedded manner are arranged between the sealing plate (19) and the clutch seat (15) and between the sealing plate (19) and the transmission shaft (3).

8. A gearbox clutch for a flexible boat according to claim 5 wherein: the clutch is characterized in that a clutch flange (7) is arranged at the front end of the clutch seat (15), a plurality of short unloading bolts (20) in threaded sleeve joint with the clutch shell (8) are arranged on the clutch flange (7), and a plurality of long unloading bolts (18) in threaded sleeve joint with the clutch shell (8) are arranged on the clutch oil cylinder (11).

9. A gearbox clutch for a flexible boat as set forth in claim 1, wherein: and bearings (1) are arranged at the two ends of the shaft gear (2) and at the two sides of the clutch component (5).